EP2781702A1 - Thermodynamic work machine - Google Patents

Abstract

The machine (1) has a hollow shaft (9) and another hollow shaft driven for rotation around a longitudinal axis during operation of the machine. The hollow shafts are sealed at front sides. The hollow shafts include passage openings, which are arranged in a circumferential wall and end in a cavity (10) and another cavity lying within the shafts, respectively. The passage openings are connected with inlets (13) and/or outlets of cylinders (2) for forming a throughflow connection during rotation of the hollow shafts around the axis. Working pistons (3) move in the cylinders.

Description

The invention relates to a thermodynamic working machine for operation with a gaseous working medium having the features of the preamble of claim 1.

Thermodynamic machines, within the meaning of the invention, that is to say machines which perform mechanical work with a working medium or make use of mechanical work, have been known for a long time and in many variants. Such machines typically have an expansion space into which a working fluid is introduced and in which it undergoes a volumetric expansion. In the expansion space movable means are arranged, which are moved in the volume expansion of the working medium and at which the mechanically useful work is performed.

In particular, internal combustion engines are known, in which a combustible gas mixture in the expansion space, there also referred to as a combustion chamber, is admitted and ignited there. During the combustion of the gas mixture, an abrupt increase in volume occurs, which drives the mechanical element in the working space. In addition to various other forms of design, such as combustion chambers in rotary piston engines, in particular cylindrical combustion chambers are known here with arranged therein, up and down moving piston. These cylindrical combustion chambers have inlet and outlet valves in order, on the one hand, to allow the mixture to be combusted to flow into the cylinder, and on the other hand to allow the exhaust gases produced during the combustion to flow out and drain off. In internal combustion engines inlet and outlet are often closed with so-called poppet valves, which are operated clocked by a camshaft. The poppet valves on the inlet side can be omitted in injection engines. There, an inflammable fuel-air mixture is injected directly into the combustion chamber and then ignited. However, the discharge of the combustion gases (exhaust gases) is also there in the usual way by opening a valve, in particular poppet valve.

In addition to the known poppet valves, other valve forms for the control of internal combustion engines or for the admission of the combustion mixture and exhaust of the exhaust gases are known. For example, describes the DD 146198 an encircling valve arrangement in the form of a rotating shaft with holes bored radially therethrough, which bores establish a connection between a feed line of the combustion mixture and the inlet into the combustion cylinder or, on the outlet side, a connection between the outlet of the cylinder and an exhaust pipe. The arrangement in the internal combustion engine shown in this publication is a series arrangement of a plurality, there four, cylinders, which are arranged so that a first continuous shaft, the inlet control, a second continuous shaft, the exhaust control operated. The valve sections of the shaft, which are assigned to each of the cylinders, are separated from each other. Inflowing fuel-air mixture can pass through the inlets controlling shaft only in the respective associated cylinder, a flow path to adjacent cylinders is closed. The same applies on the downstream side, where exhaust gas flowing out of a cylinder is transmitted only to the respective associated exhaust gas channel or the exhaust gas line.

In addition to internal combustion engines there are also thermodynamic machines which do not use a combustion of a fuel-air mixture for the performance of mechanical work due to the resulting volume expansion, but a volume expansion at a phase transition of the working medium, in particular a phase transition from the liquid to the gaseous phase. In this case, the working fluid is heated so far that it is above the phase transition temperature between the liquid and the gas phase at a predetermined pressure, the resulting gas is introduced with expansion in the expansion space and there performs mechanical work on the movable element, in the case of a cylinder as an expansion space the piston, in the case of a vane motor, for example, on the sliders of the individual cell spaces. Such thermodynamic machines that exploit volume expansion during a phase transition can be guided in a closed circuit (eg as RANKINE circulating motors) or in an open medium guide, eg operated with water vapor, which exits into the environment after expansion work has been carried out. An example of a RANKINE circulatory device in the form of a vane motor operated with a closed loop working fluid is disclosed in US Pat DE 601 23 987 T2 shown. There, the corresponding RANKINE cycle device is described as an auxiliary unit to an internal combustion engine to increase by additional mechanical work that performs this unit, the efficiency of the combined arrangement over the efficiency of a pure internal combustion engine.

Just like in the DE 601 23 987 T2 Today, there are many areas in which consideration is given to converting waste heat generated in processes into usable energy, whether in purely mechanical energy or in another conversion step in the form of electrical energy. The cogeneration, often referred to here in connection with decentralized energy generation, is a particular example of such efforts.

The invention is concerned with such considerations and aims to provide a simply designed, simply constructed and reliable thermodynamic working machine that can be operated by a working medium utilizing the volumetric expansion in the phase transition, especially in the closed circuit.

This object is achieved by a thermodynamic machine with the features of claim 1. Advantageous developments of this machine are specified in the dependent claims 2 to 10.

According to the invention, the thermodynamic working machine set up or provided for operation with a gaseous working medium has at least two cylinders each having a working piston which is movable therein. These cylinders each have an inlet and an outlet. The work machine has a first valve arrangement for opening and closing the inlets and a second valve arrangement for opening and closing the outlets. The special feature of this thermodynamic machine according to the invention is now that the first valve assembly a sealed towards their end faces, driven during operation of the machine for rotation about its longitudinal axis first hollow shaft arranged in its peripheral wall and opening in the lying within the first hollow shaft cavity Passages contains. Furthermore, according to the invention, the second valve assembly includes a sealed to its end faces, driven during operation of the machine for rotation about its longitudinal axis second hollow shaft arranged in its peripheral wall and opening into the lying within the second hollow shaft cavity through openings. The passage openings of the hollow shaft are arranged so that they can be connected upon rotation of the hollow shafts about their respective longitudinal axis with the inlets or the outlets of the cylinder to form a Durchströmverbindung. In this case, the cavity in the interior of each hollow shaft is in particular a continuous one, but at least passages are flow-connected to one another through a common cavity which come into communication with the inlets of different and adjacent cylinders.

This embodiment according to the invention, according to which the valve arrangements contain hollow shafts through which the working medium flows through the passage openings into the cylinders and work there, or in the case of the outlet valve shaft can flow out of the cylinders and be discharged, initially allowing a simple construction of the valve arrangements , Unlike, for example, poppet valves, as they are often found in conventional internal combustion engines, no complicated driving mechanism in the form of a camshaft is provided for a valve arrangement according to the invention. In addition, spring arrangements are not required, get the closing of the valves. Overall, the mechanical structure is simplified and less fragmented. In an arrangement of the cylinder in a row, here not only two, but also more cylinders, for example, four, six or even more cylinders in a row arrangement are possible, the valve assemblies can with two (each one) get along hollow shafts, one of which all Inlets serving other outlets. Through the cavity in the first hollow shaft, the incoming working fluid can distribute evenly in the hollow shaft and build a uniform pressure before the respective through openings are released to the individual cylinders by the rotating hollow shaft. Where in the operation of such a machine as an internal combustion engine, such a uniform distribution of a fuel-air mixture is detrimental and undesirable, such a uniform distribution of a working medium in a working machine considered here, the volume changes during the phase transition in particular from liquid to gaseous for the implementation mechanical work, to a better result, to a particularly smooth running of the machine and also to a high efficiency. Because the fact that the expanding working fluid already rests with high pressure in the cavity of the hollow shaft, this can get on the shortest route and just at high pressure in the working space, where they work directly with high impact. It does not first have to overcome a longer distance between a supply line and the actual inlet of the working space and pressure is built up at the beginning of a work cycle.

Analogous considerations apply to the second hollow shaft, in which the discharged from the cylinders, relaxed working medium also propagates in the entire cavity of the hollow shaft, insofar as can be particularly good and simplified dissipated.

The design with the hollow shafts according to the invention is also particularly compact. Finally, this design allows the use of known from the field of internal combustion engine technology. For example, internal combustion engines can be retrofitted with simple means and provided with the inventively provided valve arrangements with the hollow shafts. For this purpose, only the cylinder heads are to be replaced in an array of cylinders in an internal combustion engine against corresponding valve assemblies connected to a cylinder head section with hollow shafts, the cylinder itself can be adopted without significant changes. Such retrofitting is not only possible in terms of a new building, in principle, even existing internal combustion engines can be converted accordingly to thermodynamic machines according to the invention with a few simple steps and with the result of a machine with high efficiency. In this way, for example, for a decentralized power supply, e.g. existing and no longer used internal combustion engines used in the field of combined heat and power, are overhauled and rebuilt and then operated as thermodynamic working machines according to the invention, e.g. to drive electric generators.

Advantageously, the passage openings are formed slot-shaped in the hollow shafts and have a longitudinal extent of the slot parallel to the longitudinal axis of the respective hollow shaft. Such a configuration ensures by the longitudinal extent of the slots that a sufficient cross-sectional area for a rapid influx of sufficient volume or stream of the expanding gaseous working medium into the cylinder or a discharge of the expanded and expanded working medium can be made from the cylinders. On the other hand, by the slot width, which can be chosen very targeted here, a very precise control of opening and closing time of the inlets or outlets of the cylinder, which is for achieving a smooth running and high efficiency of the machine of great importance.

Since typically the inlets of the cylinders require shorter opening times for the sudden filling with the expanding and pressurized gaseous working fluid, the outlets for expelling the expanded and expanded working medium require a longer opening time, the passage openings are advantageously designed such that the passage openings of the first hollow shaft in the circumferential direction of the first hollow shaft having a small opening width than the seen in the circumferential direction of the second hollow shaft opening width of the passage openings of this second hollow shaft. The design can be, for example, such that it causes opening of the inlets in a position 10 ° before top dead center with respect to a rotational position of a connected via connecting rods with the piston crankshaft, the inlets closes at about 30 ° after top dead center, so that results in an opening interval in the interval of about 10 ° before top dead center to 30 ° after top dead center. The setting of the passage openings on the second hollow shaft can be designed, for example, so that the outlet opens with respect to the rotational position of the crankshaft at about 10 ° before bottom dead center and the outlets until shortly before the opening of the inlets, in this case to about 10th ° keeps open before top dead center.

In a further advantageous embodiment of the invention, the working machine can be designed so that in the first and the second hollow shaft per cylinder two each with the inlet and the outlet of the respective cylinder during rotation of the respective hollow shaft cooperating through openings are provided in the peripheral wall of the hollow shaft which are diametrically opposed to each other. As a result, two work cycles, that is to say periods of time in which expanding gas is conducted into the cylinder and mechanical work is performed, take place per entire revolution of the respective hollow shaft. In addition, a supply line for the pressurized and to be introduced into the cylinder, expanding gas may be arranged in a position opposite to the inlet, so that when the one of the passage openings opens the respective inlet of the cylinder, the diametrically opposite passage opening releases the supply line. Analogously, on the outlet side, an outflow line for expanded and expanded gaseous working medium may be provided in a position opposite the outlet, so that upon opening of the outlet by cooperation of the one passage opening with the outlet at the same time the passage opening opposite this passage opening for a connection to the discharge channel or discharge line releases.

The valve arrangement of the working machine according to the invention is particularly simple if, as provided according to an advantageous development, the hollow shafts are rotatably arranged in a block sealed against the cylinders and have the inlets and the outlets sealed to the end faces. With sealed to the end faces here is a seal between the respective rotating hollow shaft and a receptacle in the block meant so that escape at this point no pressurized working fluid and thereby the efficiency of the machine can be reduced. Such a block can be easily produced on the one hand and forms on the other hand in addition to the storage of the hollow shafts and thus the design of the valve assembly at the same time the sealing of the cylinder in the upper section, so represents the cylinder head gasket. In the block can then also the inlet and outlet openings of the Cylinder be formed, which cooperate with the passage openings of the hollow shafts for the valve function. By replacing the conventional cylinder heads with the conventional valve assemblies (such as poppet valves) and provided for valve actuation cam against a valve assembly according to the invention forming block with the hollow shafts arranged thereon and connection of the hollow shafts for rotation can easily a conventional internal combustion engine with a cylinder bank arrangement to a thermodynamic work machine according to the invention, which works with a gaseous relaxing working medium and without combustion, be converted.

As already mentioned above may be provided in the machine according to the invention that the working piston of the cylinder are connected via connecting rods with a crankshaft, which is driven in operation by the up and down movement of the working piston for rotation. In this case, the crankshaft can furthermore advantageously be coupled to the rotary drive of the hollow shafts with these hollow shafts with advantage. This makes it possible to achieve a coordinated control of the valve opening with respect to the position of the piston in the respective cylinder. This coupling between the crankshaft and the hollow shafts may be formed such that a speed ratio between the crankshaft and the hollow shafts, i. each one of the hollow shafts, of 2: 1 yields. Furthermore, this coupling can take place such that the hollow shafts are coupled to one another via a coupling element for uniform rotation. This can be effected with advantage by a gear transmission which couples the hollow shafts with each other for opposite rotation at the same speed.

As already mentioned and explained, the thermodynamic machine according to the invention is particularly suitable for operation with a guided in a closed circuit working fluid. For this purpose, the working machine is then advantageously connected to a closed circuit for the working medium. Such a work machine may e.g. be used to with the closed-cycle working medium waste heat from other processes, e.g. Waste heat from the combustion of fuels for the heat recovery or waste heat from industrial plants or waste heat from electric power plants are operated to continue to use this waste heat and to obtain mechanical energy, with the mechanical energy, for. to drive more electric generators.

In an arrangement of more than two cylinders in a row whose inlets and outlets are opened and closed controlled by the hollow shaft having the passage openings, a setting of the working piston in the cylinders and the position of the arrangement of the passage openings in the hollow shafts is designed be that the different cylinders are running with different bars. So it is particularly appropriate here for a smooth running of the working machine, a first part, ideally half, of the cylinder in one working stroke to drive, while the second part, ideally the second half of the cylinder performs a cycle of discharging the relaxed working medium. Thus, the driving process performed in two cycles (venting the gas in the cylinder and causing work, expelling the expanded gaseous working fluid from the cylinders as the pistons move upwards) is carried out at any time on at least part of the cylinders, ideally halfway the cylinder is a power stroke, according to driving force on a piston downstream element, such as the crankshaft, is transmitted.

Fig. 1

schematisch eine Schnittansicht durch eine thermodynamische Arbeitsmaschine in einer erfindungsgemäßen Ausgestaltung mit Hohlwelle (hier die Hohlwelle für die Einlassventilsteuerung);

Fig. 2

im Ausschnitt einen Querschnitt durch einen Arbeitsraum mit darin angeordnetem Zylinder einer erfindungsgemäße thermodynamischen Arbeitsmaschine mit den Hohlwellen der Ventilanordnungen auf Einlass- und Auslassseite;

Fig. 3

in einer anderen Darstellung eine mögliche Anordnung eines Ventilblocks mit den erfindungsgemäß vorzusehenden Hohlwellen in einer thermodynamischen Arbeitsmaschine gemäß der Erfindung;

Fig. 4

mit einer Ansicht auf die den Arbeitsräumen zugewandte Unterseite den Ventilblock auf Fig. 3 ohne darin eingesetzte Hohlwellen;

Fig. 5

in einer Längsschnittdarstellung die Hohlwelle der Auslassventilanordnung ohne aufgesetzte Endkappen;

Fig. 6

die Hohlwelle aus Fig. 5 in einer dreidimensionalen Ansicht;

Fig. 7

in einer der Fig. 5 vergleichbaren Schnittansicht die Hohlwelle der Eingangsventilanordnung, wiederum ohne aufgesetzte Endkappen;

Fig. 8

die Hohlwelle aus Fig. 7 in einer der Fig. 6 vergleichbaren dreidimensionalen Darstellung;

Fig. 9

die Hohlwelle der Auslassventilsteuerung in einer Aufsicht und mit montierten Endkappen;

Fig. 10

die Hohlwelle der Einlassventilsteuerung in einer der Ansicht in Fig. 9 vergleichbaren Ansicht mit aufgesetzten Endkappen; und

Fig. 11

in zwei Ansichten a und b zwei unterschiedliche Gestaltungsformen der die Hohlwellen stirnseitig verschließenden Endkappen mit daran angeformten Antriebszapfen.

Further advantages and features of the invention will become apparent from the following description of an embodiment with reference to the accompanying figures. Showing:

Fig. 1

schematically a sectional view through a thermodynamic machine in an embodiment according to the invention with a hollow shaft (here, the hollow shaft for the intake valve control);

Fig. 2

in section a cross section through a working space with arranged therein cylinder of a thermodynamic machine according to the invention with the hollow shafts of the valve assemblies on the inlet and outlet side;

Fig. 3

in another illustration, a possible arrangement of a valve block with the invention to be provided hollow shafts in a thermodynamic machine according to the invention;

Fig. 4

with a view of the workrooms facing the underside of the valve block Fig. 3 without hollow shafts inserted therein;

Fig. 5

in a longitudinal sectional view of the hollow shaft of the Auslassventilanordnung without patch end caps;

Fig. 6

the hollow shaft out Fig. 5 in a three-dimensional view;

Fig. 7

in one of the Fig. 5 comparable sectional view of the hollow shaft of the input valve assembly, again without patch end caps;

Fig. 8

the hollow shaft out Fig. 7 in one of the Fig. 6 comparable three-dimensional representation;

Fig. 9

the hollow shaft of the exhaust valve control in a plan view and with mounted end caps;

Fig. 10

the hollow shaft of the intake valve control in one of the view in Fig. 9 comparable view with attached end caps; and

Fig. 11

in two views a and b two different forms of the hollow shafts end-capping end caps with drive pin formed thereon.

In the figures, schematic representations for possible design variants of the invention, in particular the thermodynamic machine according to the invention and its valve arrangement are shown. With reference to these figures, a possible embodiment of the invention will be explained below. The figures are by no means to scale or complete construction drawings, but merely give the operating principle and the essential features of the embodiment of the invention again and serve only for explanation.

In Fig. 1 is shown in a longitudinal sectional view schematically a thermodynamic machine 1 in the inventive design. This thermodynamic machine 1 has in a row arrangement a total of four cylindrical work spaces 2, in which pistons 3 are arranged movable up and down and sealed in the circumferential direction, as is well known for such machines. The pistons 3 are connected via connecting rods 4 with a crankshaft 5, which extends in a known manner cranked and together with the connecting rods 4 of the implementation of a linear movement of the piston 3 in a rotational movement, which executes the crankshaft 5 serves.

In the Fig. 1 the inlet valve arrangement is shown, via which a working medium can be introduced into the cylindrical working spaces 2. An outlet valve arrangement likewise installed in the working machine 1 according to the invention is not shown in this illustration. The inlet valve arrangement comprises a hollow shaft 9, which is arranged in a valve block 6 and fits precisely into a shaft bearing 8 formed in the valve block 6, in which it can rotate. The hollow shaft 9 has in its interior a continuous cavity 10, the circumference by an outer wall 11 (see. Fig. 2 ) of the hollow shaft 9 is limited. The front side, the hollow shaft 9 is also closed. The manner in which this closure is carried out will be described below in particular with reference to the FIGS. 9 to 11 be explained in more detail.

In the outer wall 11, the hollow shaft 9 through openings 12 in the form of extending in the longitudinal direction of the hollow shaft 9 slots. In this case, at corresponding longitudinal positions of the hollow shaft 9 are arranged in each case diametrically opposite substantially identically shaped slots to slot pairs. Along its longitudinal direction, the hollow shaft 9 in its outer wall 11 a total of four such pairs of slots. The diametral orientation of the two along the longitudinal extent of the hollow shaft 9 outboard slot pairs is the same. The two inwardly located with respect to the longitudinal extent of the hollow shaft 9 pairs of slots are also arranged the same in its diametrical orientation, but at 90 ° angularly offset from the orientations of each located to the axial ends of the hollow shaft 9 pairs of slots.

In the Fig. 1 It can be seen that in the rotational position shown there, the hollow shaft 9 is located in such a rotational position that the adjacent to the axial ends of the hollow shaft 9 through openings 12 on the one hand the supply 7 and on the other hand, an inlet opening 13 in the respective working space 2 of the outside aligned cylinder. Thus, here indicated by the arrows, working medium from the supply 7 flow into the cavity 10 of the hollow shaft 9 and penetrate from there into the respective working space 2 of the two outer cylinder and there the respective piston 3 in a in the Fig. 1 driving direction shown below. Via a toothed belt 14, the placed on a camshaft 5 mounted on the toothed belt pulley 15 and arranged on a hollow shaft 9, rotatably connected with this timing belt pulley 16, the hollow shaft 9 is clocked at the speed of the crankshaft 5 driven for rotation. As a result of this rotation, the positions of the passage openings 12 change, with the result that the work spaces 2 of the cylinders arranged on the outside or the work spaces 2 of the inner cylinder pair are alternately connected to the respective feed lines 7. The coupling between crankshaft 5 and hollow shaft 9 ensures that a corresponding timing is maintained, in which the connection of the supply lines 7 with the associated work spaces 2 only takes place when the piston 3 in a like in Fig. 1 located in the region of top dead center with respect to the two outer piston 3 position shown. Through the continuous cavity 10 in the hollow shaft 9 can be through the various supply lines 7 (in principle, only a single supply line 7 may be provided here) flowing working medium spreads uniformly and is already inside the hollow shaft 9 at high pressure. As soon as the valve is opened to the associated working space 2 via the passage openings 12, which are brought into coincidence with corresponding inlet openings 13 of the associated working spaces 2, the working medium can flow into the working space over a short distance and already at full pressure and there with a high pressure Efficiency work. In one embodiment, the pressure of the working medium, with which this is present in the supply line 7 and in the cavity 10 of the hollow shaft 9 is, for example, in the range of 10 bar.

The crankshaft 5 and the hollow shaft 9 are in the in Fig. 1 example shown coupled in a 1: 1 translation, ie they each run at the same rotational speed. Characterized in that at the respective positions of the associated working spaces 2, the hollow shaft 9 diametrically opposite each other on its outer wall 11 has two passage openings 12, is fed at each half rotation of the hollow shaft 9 working fluid in the working space 2. This thermodynamic work machine thus operates on the two-stroke principle.

In Fig. 2 is in a cross section a section of the working machine 1 according to Fig. 1 shown. There is good to see that in the valve block 6 in addition to the basis of Fig. 1 already described in more detail hollow shaft 9 with the constituent of the inlet valve assembly forming passage openings 12 in a further formed in the valve block 6 shaft bearing 17, a second hollow shaft 18 is arranged. This, too, has a continuous cavity 19 which is bounded on the circumference by an outer wall 20 of the hollow shaft 18. In the outer wall 20 of this further hollow shaft 18 through openings 21 are also provided, which are also formed slit-shaped and extending in the longitudinal direction of the hollow shaft 18. These openings 21 are located at diametrically opposite positions in the outer wall 20 of the hollow shaft 18. Also in this hollow shaft 18 a total of four pairs of diametrically opposed passage openings 21 are arranged, in which case the respective axial end of the hollow shaft 18 adjacent pairs of each other opposing slot-shaped passage openings 21 in the same orientation, the intermediate pairs located therebetween are arranged at a 90 ° angle to this shifted alignment. In operation, the two hollow shafts 9 and 18 are oriented so that associated pairs of passage openings 12 and 21, which are associated with a working space 2, are arranged displaced by a 90 ° angle, as shown in FIG Fig. 2 easy to recognize. It can also be seen there that the shaft bearing 17 has a connection to a discharge line 22, which, when a corresponding passage opening 21 in the outer wall 20 of the hollow shaft 18 is opposite this, is released. Furthermore, an outlet opening 23 can be seen at the upper end of the working space 2, which can also be brought into coincidence with one of the passage openings 21 of the hollow shaft 18, so as to release an outlet from the working space 2. The second hollow shaft 28 is (not shown here) connected to the crankshaft 5 in a 1: 1 ratio to the rotary drive, so that it rotates at the same speed as the crankshaft 5 and also like the hollow shaft 18 in the shaft bearing 17. By offset by 90 ° relative to the arrangement of the hollow shaft 18 arrangement of the hollow shaft 18 is achieved that in the region of the bottom dead center of the piston 3 in the working space 2, the outlet opening 23 is opened by a passage opening 21 and the discharge line 22 is released. Thus, 3 relaxed working fluid can be ejected when re-moving the piston. For this purpose, in particular, the passage openings 21 in the second hollow shaft 18 in the circumferential direction are formed wider (in the Fig. 2 only a schematic representation is given), so that sufficient time remains for the ejection process to free the working space 2 without a resistance of relaxed working medium. The width seen in the circumferential direction of the slot-shaped passage openings 12 in the hollow shaft 18 on the inlet valve side, however, are kept small to cause here a sudden application of the working space 2 with pressurized working fluid with a short opening time.

In Fig. 3 It can be seen how the connection of the second hollow shaft 18 with the crankshaft 5 is accomplished. The first hollow shaft 18 is connected on one side with the toothed belt pulley 16, on the opposite side its second axial end is connected to a gear 24. This gear meshes with a gear 25 which is placed on the adjacent axial end of the second hollow shaft 18 and provided with the same toothing. As a result, a 1: 1 coupling of the two hollow shafts 9 and 18 is achieved.

In Fig. 4 is a view of the valve block 6 of the working spaces 2 facing bottom shown. To recognize there are the inlet openings 13 and outlet openings 23, which create a connection to the respective workrooms 2. Evident is also a sealing groove 26 which encloses these openings in the closed course and in which a corresponding seal for sealing this area of the cylinder heads is introduced. Further, in this illustration, the shaft bores 8 and 17 formed as cylinder bores for the hollow shaft 9 and 18 (not shown in this illustration) can be well seen.

In the FIGS. 5 and 6 is in two different representations, once a longitudinal representation ( Fig. 5 ) and once a three-dimensional view obliquely from a front side once again the hollow shaft 18 of the exhaust valve assembly shown. Good to see here are the openings 21, which are arranged in pairs opposite each other and also the continuous cavity 19. In particular, the comparison with the similar representations of the hollow shaft 9 in the FIGS. 7 and 8 shows that in the hollow shaft 18, the slot-shaped passage openings 21 extend with a substantially larger width in the circumferential direction of the outer wall 20 for a correspondingly long-term controlled discharge time.

In the FIGS. 7 and 8 is, as already mentioned, in the FIGS. 5 and 6 comparable representations, the hollow shaft 9 of the intake valve assembly shown again. Again, this hollow shaft 9 is shown without its axial ends occluding closing elements (end caps). Again, it can be clearly seen how the slot-shaped passage openings 12 are arranged in a staggered arrangement in pairs to each other in the outer wall 11 and introduced. The slot widths of the passage openings 12 seen in the circumferential direction are significantly smaller here than in the case of the hollow shaft 18, so that short inlet or control times can be achieved for the intake operation.

In the FIGS. 9 and 10 are the hollow shafts 18 and 9 again shown in a side view with attached end caps 27 and 28 (with molded pins), which cause a closure of the end faces of the hollow shafts and thus completion of the cavities and on the other an arrangement of the gears or the To allow the toothed belt pulley on the pin and thus a transmission of the rotary drive. These end caps 27 and 28 are in Fig. 11a or b again shown in an enlarged view. <B><u> REFERENCE LIST </ u></b> 1 working machine 2 working space 3 piston 4 connecting rod 5 crankshaft 6 manifold 7 feed 8th shaft bearing 9 hollow shaft 10 cavity 11 outer wall 12 Through opening 13 inlet port 14 toothed belt 15 Timing pulley 16 Timing pulley 17 shaft bearing 18 hollow shaft 19 cavity 20 outer wall 21 Through opening 22 discharge 23 outlet 24 gear 25 gear 26 sealing groove 27 endcap 28 endcap

Claims (10)

Thermodynamic working machine for operation with a gaseous working medium having at least two cylinders (2) each having a working piston (3) movable therein, each having an inlet (13) and an outlet (23), and having a first valve arrangement (8, 9 ) for opening and closing the inlets (13) and a second valve arrangement (17, 18) for opening and closing the outlets (23), characterized in that the first valve arrangement (8, 9) is sealed off towards its end faces during operation the working machine (1) for rotation about its longitudinal axis driven first hollow shaft (9) arranged in its peripheral wall (11) and in which within the first hollow shaft (9) lying cavity (10) opening out through openings (12) and that the second valve assembly (17, 18) a sealed to their end faces, during operation of the working machine (1) for rotation about its longitudinal axis driven second hollow shaft (18) with in order arranged receiving wall (20) and in which within the second hollow shaft (18) lying cavity (19) opening through openings (21), wherein the passage openings (12, 21) of the hollow shafts (9, 18) are arranged such that they rotate the hollow shafts (9, 18) about their respective longitudinal axis with the inlets (13) and the outlets (23) of the cylinder (2) are connectable to form a Durchströmverbindung. Work machine according to claim 1, characterized in that the passage openings (12, 21) are slot-shaped with a longitudinal extent parallel to the longitudinal axis of the respective hollow shaft (9, 18). Work machine according to one of the preceding claims, characterized in that the passage openings (12) of the first hollow shaft (9) in the circumferential direction of the first hollow shaft (9) have a smaller opening width than in the circumferential direction of the second hollow shaft (18) seen opening width of the passage openings ( 21) of this second hollow shaft (18). Work machine according to one of the preceding claims, characterized in that in the first (9) and in the second (18) hollow shaft per cylinder (2) two each with the inlet (13) and the outlet (23) of the respective cylinder (2 ) on rotation of the respective hollow shaft (9, 18) cooperating passage openings (12, 21) in the peripheral wall (11, 20) of the hollow shaft (9, 18) are provided which are diametrically opposed to each other. Work machine according to one of the preceding claims, characterized in that the hollow shafts (9, 18) in a relative to the cylinders (2) sealed, the inlets (13, 23) and the outlets having block (6) arranged rotatably and towards the end faces are sealed. Work machine according to one of the preceding claims, characterized in that the working piston (3) of the cylinder (2) via connecting rods (4) with a crankshaft (5) are connected and these drive in operation for rotation and that the crankshaft (5) for rotation -Antrieb the hollow shafts (9, 18) coupled with these. Work machine according to claim 6, characterized in that the coupling between the crankshaft (5) and the hollow shafts (9, 18) is formed such that a speed ratio between the crankshaft (5) and the hollow shafts (9, 18) of 2: 1 results. Work machine according to one of claims 6 or 7, characterized in that the hollow shafts (9, 18) via a coupling element (24, 25) are coupled to each other for uniform rotation. Work machine according to claim 8, characterized in that the hollow shafts (9, 18) are coupled via a gear transmission with each other for opposite rotation at the same speed. Work machine according to one of the preceding claims, characterized in that it is connected to a closed circuit for the working medium.

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