WO1999022118A1

WO1999022118A1 - Device for conveying a medium or propulsion through a medium

Info

Publication number: WO1999022118A1
Application number: PCT/EP1998/006829
Authority: WO
Inventors: Ernst Beck
Original assignee: Ernst Beck
Priority date: 1997-10-28
Filing date: 1998-10-28
Publication date: 1999-05-06
Also published as: ATE222638T1; DE19747445A1; DE59805259D1; CN1276848A; WO1999022118B1; EP1034356A1; CA2308709A1; EP1034356B1; JP2001521100A; KR20010031243A

Abstract

The invention relates to a conveyor device for a medium, especially for a gas or liquid, comprising a piston/cylinder unit, whereby the medium is suctioned by means of the movement of a piston and conveyed by means of an opposite piston movement in addition to being based on a valve device function. The movement of the piston is carried out by means of a bearing (precision bearing) and the bearing (precision bearing) is located outside the cylinder (cylinder chamber, combustion chamber).

Description

Device for conveying a medium or for driving through a medium

description

The invention relates to a device for conveying a liquid or gaseous medium or for driving through a medium according to the preamble of claim 1.

Such devices are known for example as compressors. The known compressor has a piston-X cylinder unit, in which the piston is moved up and down by means of a piston rod and a crank mechanism. A valve arrangement, which consists of two check valves, which are assigned to the cylinder unit, ensures that ambient air is sucked into the cylinder chamber when the piston U moves downward and that the suctioned-in air is expelled as conveying air during the subsequent upward movement of the piston. One valve operates during the suction process and the other valve functions during the exhaust process. The up and down movement of the piston is realized by driving the crank mechanism by means of a drive unit, for example an electric motor. In the known arrangement Disadvantage that to avoid seizure of the piston, the sliding surface of the piston on the inner wall of the cylinder must be provided with a lubricant, for example with a thin oil film. This has the consequence that the conveying air can be contaminated by oil residues, which is particularly problematic in the food industry, in which the compressed air generated by the compressor is used. However, it is also necessary in other branches of industry to provide clean conveying air which has no lubricant residues.

The invention has for its object to provide a device of the type mentioned, which does not have these disadvantages.

This object is achieved in that the movement of the piston is guided by means of a bearing and that the bearing is located outside the cylinder. Due to this construction, it is possible to optimally guide the piston in the bearing so that it runs through a precisely defined and exact path of movement. The bearing can be designed in any way. It is not a problem if the bearing contains a lubricant, for example bearing grease or the like, since it is arranged outside the cylinder and consequently no residues of the lubricant or the like can get into the cylinder and thus into the pumped medium. Since the piston thus has a separate bearing, unlike in the prior art, it does not have to guide itself in the cylinder, so that friction of the piston on the inner wall of the Cylinder is completely avoided. Because of the bearing, the piston can be guided so precisely that it runs without lubricant in the cylinder and maintains an extremely small distance from the inner wall of the cylinder, the distance being so small that leakage losses are largely avoided. Additional sealing means, for example disks made of metal, as are used in known conveying devices and which are arranged in the gap between the piston and the inner wall of the cylinder, can be dispensed with.

According to a development of the invention, it is provided that the piston performs a partial circular movement about a pivot point. In particular, it is provided that the piston is formed on a rotating part so that it can carry out the above-mentioned partial circular movement.

Preferably, the mentioned rotating part has the bearing, the piston being radially offset from the pivot point. The rotary part therefore carries out an oscillating movement for the reciprocating movement of the piston, the piston, which is offset radially outward relative to the pivot point of the rotary part, runs through a partial circular path. Since the rotating part is precisely guided by means of the bearing arranged outside the cylinder, the piston moves along an exact, defined path, which prevents inadmissible frictional forces from occurring against the inner wall of the cylinder. According to a development of the invention, it is provided that a first cylinder wall facing a first end face of the piston is penetrated by at least one check valve. Alternatively, it is also possible for a first cylinder wall facing a first end face of the piston to be penetrated by at least two non-return valves which have opposite flow directions. In the former case, the check valve ensures that this allows the medium to be sucked into the cylinder space by opening the piston by means of a corresponding piston movement. The piston is then moved back, preferably having at least one check valve passing through it, so that the pumped medium flows through the piston and then - with a further piston stroke - exits through a further check valve. In a further development of the invention, this further check valve passes through a second cylinder wall facing the other, second end face of the piston.

In the above-mentioned second possibility, in which two non-return valves penetrate the cylinder wall, the medium is sucked in through one of the two non-return valves during a first piston movement, and in the subsequent piston return movement, the medium is fed through a feed line to the second non-return valve. The two check valves thus ensure that a suction process through a suction line and a discharge process through a discharge line are carried out during a piston stroke. If corresponding cylinder walls, each with two non-return valves, are located on both sides of the piston, that is to say on its two end walls, a suction operation of the medium can be carried out on one piston end side and an ejection operation on the other piston end side.

To achieve the object, a device for driving through a medium, in particular a two-stroke internal combustion engine, is also proposed with the features of claim 13. This is characterized in that the movement of the piston is guided by means of a bearing and that the bearing is arranged outside the combustion chamber. Due to this construction, it is possible to optimally guide the piston in the bearing so that it runs through a precisely defined and exact path of movement. The bearing can be designed in any way. It is not a problem if the bearing contains a lubricant, for example bearing grease or the like, since it is arranged outside the combustion chamber and consequently no residues of the lubricant or the like can get into the combustion chamber and thus into the exhaust gases of the internal combustion engine. Since the piston thus has a separate bearing, unlike in the known internal combustion engines, it does not have to lead itself in the combustion chamber formed by a recess, bore or the like, so that friction of the piston on the combustion chamber wall is preferably complete, but at least largely is avoided. Due to the bearing, the piston can be guided so precisely that it runs in the combustion chamber without lubricant and thereby an extremely small NEN distance to the combustion chamber wall, the distance is so small that leakage losses are largely avoided.

An embodiment of the internal combustion engine is particularly preferred, which is characterized in that the piston is guided in the combustion chamber without a seal relative to the combustion chamber wall. Additional sealants, for example sealing rings, such as are provided in the known internal combustion engines for sealing the gap between the piston and the combustion chamber wall, are not required. The gap between the side surface of the piston and the combustion chamber wall is extremely thin, so that leakage losses alone and / or due to a relatively large length of the side surface of the piston can be avoided.

The drawing illustrates the invention using exemplary embodiments, namely:

FIG. 1 shows a perspective view (obliquely from above) of a conveyor device,

FIG. 2 shows a perspective view obliquely on the underside of the conveyor,

FIG. 3 shows a side view of the conveyor device (partly in section),

4 top views of a piston / cylinder to 9 unit of the conveyor in different piston positions, FIG. 10 shows a side view of an exemplary embodiment of an internal combustion engine (partly in section),

11 each shows a plan view of a piston component arranged in and 12 a combustion chamber in different piston positions,

FIG. 13 shows a plan view of an exemplary embodiment of a first printing plate, and

Figure 14 is a side view of an embodiment of a connection plate.

FIG. 1 shows a conveyor device 1 which, in accordance with the exemplary embodiment here, is designed as a compressor. It has a housing 2 and a piston / cylinder unit 3. A drive shaft 4 is rotatably mounted in the housing 2, to which a drive unit (not shown), for example an electric motor, can be coupled. At the free end of the drive shaft 4, a crank disc 5 is rotatably arranged so that an eccentric 6 (Figure 2) is formed. A fork piece 8 is pivotally mounted in an eccentrically located receiving recess 7, the fork arms 9 of which are pivotably connected to a block piece 11 about an axis 10 which runs horizontally in FIG. The block piece 11 is rotatably connected to a piston shaft 12. The piston / cylinder unit 3 has a cylinder 14 which has a circular-hollow cylindrical lower part 15 and a cylinder cover 16. The cylinder cover 16 is designed as a circular plate which is screwed to the pot-shaped lower part 15 using suitable means, for example with machine screws. A precision bearing 17 (FIG. 3) is arranged in the housing 2 and rotates the piston shaft 12 exactly and also in the exact axial position.

It can be seen from FIGS. 4 to 6 that in the cylinder 14 the piston component 18 of the piston / cylinder unit 3 is rotatably guided around the piston shaft 12 along a partial circular movement. The piston component 18 has a first piston 19 and a second piston 20, both of which are offset radially outward from the pivot point 21 of the piston component 18. The fulcrum 21 lies on the axis of rotation of the piston shaft 12. The piston component 18 has a circular central part 22, from which the first and the second pistons 19, 20 extend radially outward in a wing-like manner, the respective pistons 19, 20 extending to the inside 23 of the cylinder 14 extends. The side surface 24 of the respective piston 19, 20 is therefore convexly curved in accordance with the inner curvature of the inside 23. The inside 23 faces the side surface 24 without contact with extremely little play, such that a seal is created there. As can be seen from FIGS. 4 to 6, no separate sealing means are provided in this area because they are not required. The sealing of the gap between the side tenflache 24 of the respective piston 19, 20 and the inner wall of the cylinder 14 takes place exclusively with the help of the small play between the two components and the relatively large arc length of the side surface 24, which is formed in a circular section in this embodiment. Inside the piston / cylinder unit 3 there are cylinder walls 25, 26, 27 and 28 which are arranged in a stationary manner. The cylinder walls 25 to 28 are pressure-tightly connected to the bottom 29 of the lower part 15 and also pressure-tight to the inside 23. The respective inner side 30 of each cylinder wall 25 to 28 is spaced apart from the outer periphery 31 of the central part 22 with a slight clearance, so that although the piston component 18 can move about the pivot point 21, a seal is formed between the surfaces mentioned. Separate sealants can also be dispensed with here. In a corresponding manner, each piston 19, 20 is arranged opposite to the inside of the bottom 29 and the inside of the cylinder cover 16 with only very little play, so that overall the situation arises that the two pistons 19 and 20 due to the bearing of the piston component 18 by means of of the precision bearing 17 can be moved in a contact-free but sealing manner in the respective cylinder space 32, 33. The cylinder space 32 lies between the cylinder walls 25 and 26; the cylinder space 33 is located between the cylinder walls 27 and 28. Due to the extremely thin gap between the side surface 24 of the respective piston 19, 20 and the outer periphery 31 of the central part 22, the cylinder derraum 32, 33 separated by the pistons 19 and 20 from each other.

It can also be seen from FIGS. 4 to 6 that the cylinder walls 25 to 28 are penetrated by bores 34 in which there are check valves 35, 36, 37 and 38 provided with helical springs. As an alternative, tongue or diaphragm valves or the like can also be used. Furthermore, the two pistons 19 and 20 are penetrated by through holes 39 in which check valves 40, 41, 42 and 43 are arranged. According to FIG. 1, the cylinder cover 16 is penetrated by a medium inlet opening 44 and by a medium outlet opening 45. For the sake of clarity, these two openings can also be seen with a broken line in FIGS. 4 to 6. They are arranged in such a way that the medium inlet opening 44 is located between the two cylinder walls 25 and 27 and the medium outlet opening 45 between the two cylinder walls 26 and 28 and in each case between the outer periphery 31 and the inside 23 of the circular-hollow cylindrical lower part 15. Chambers are therefore formed in these areas, the chamber associated with the medium inlet opening 44 forming a suction chamber 46 and the chamber associated with the medium outlet opening 45 forming an ejection chamber 47.

The following function results:

If the drive shaft 4 by means of a suitable

Drive (not shown) according to arrow 48

(Figure 4) rotated, the crank disc 5 The fork piece 8 also acts as an eccentric, whereby the block piece 11 is set into an oscillating back-and-forth movement, that is, the piston component 18 carries out an oscillating movement around the piston shaft 12, that is to say about the pivot point 21 . Thus, during this movement, the respective piston 19 or 20 is displaced within the cylinder space 32 or 33 such that, starting from FIG. 4-, for example, the piston 19 first lies opposite the cylinder wall 25, then moves in the direction of the cylinder wall 26 (FIG. 5 ) and finally opposite the cylinder wall 26 with only a very small distance (FIG. 6). The further movement then takes place in the reverse manner, that is to say the piston 19 moves back in the direction of the cylinder wall 25. The same applies to the piston 20, which moves back and forth between the two cylinder walls 27 and 28. This oscillating movement has the result that, starting from the illustration in FIG. 4-, the piston 19 moves away from the cylinder wall 25, as a result of which it sucks in air through the medium inlet opening 44 and the suction chamber 46 into the cylinder chamber 32 while the check valve 35 is opened. When the piston 19 reaches the position shown in FIG. 6, the suction phase is complete and the piston 19 moves back in such a way that the intake air located in the cylinder chamber 32 is slightly compressed, in such a way that the two check valves 40 and 41 in the piston 19 open automatically due to the inertia, which essentially moves the air volume to the other side of the piston, that is, it flows through the through-hole tion 39. If the piston 19 is moved again in the direction of the cylinder wall 26 during the next piston stroke, the air volume is conveyed into the discharge chamber 47 by opening the check valve 36 and from there to the medium outlet opening 45. In the case of the latter conveying movement, a suction process takes place simultaneously on the other side of the piston 19. It remains to be noted that the check valves 40, 41 in the piston also automatically close again with the aid of inertia. Corresponding processes take place in the piston 20, that is, the conveyor device 1 is able to deliver a high delivery rate due to the two pistons 19 and 20.

FIGS. 7 to 9 show a further exemplary embodiment of a conveying device which differs from the above-mentioned exemplary embodiment only in terms of the arrangement of the check valves, so that only this change will be discussed below. It can be seen that the cylinder walls 25 to 28 are each penetrated by two bores 34, in which check valves 51, 52, 53, 54, 55, 56, 57 and 58 are arranged. The check valves 51 and 52 or 53 and 54 or 55 and 56 or 57 and 58 lie with opposite flow directions to one another, so that the one check valve forms an intake valve and the other check valve forms a pressure valve. Otherwise, the same parts - as far as can be seen - as in Figures 1 to 6 with the same Provide reference numerals. In this respect, reference can be made to their description.

According to FIGS. 7 to 9, the following function results:

If the piston 19 moves counterclockwise, the check valve 51 opens, so that air is sucked into the cylinder chamber 32 from the suction chamber 46. If the piston 19 then moves clockwise, the sucked-in air is fed through the non-return valve 52 to a pressure line 59 connected there, indicated only by dashed lines, which leads to the medium outlet opening 45. The same applies to the further check valve pairs with their associated cylinder walls 26, 27 and 28, so that a total of quasi four cylinder spaces are formed. The respective suction takes place via the medium inlet opening 44 and the respective discharge to the medium outlet opening 45, corresponding suction or pressure lines not shown in the figures being used.

Finally, it should be noted that it is possible with the conveying device 1 to convey several, even different, media at the same time. Each piston 19 and 20 with its associated cylinder space each form a separate unit. The respective cylinder spaces 32 and 33 are then each assigned a medium inlet opening 44 and a medium outlet opening 45. It is also easily possible to provide more than two pistons. Overall, depending on the number of pistons, the same Number of media to be funded. In a preferred embodiment variant of the conveying device, in which it has a plurality of pistons, it is provided that the amount of medium conveyed by pivoting the individual pistons is of the same size. As a result, the conveying device can advantageously also be used as a metering pump, for example for filling liquid foods, for example milk.

It is also clear that the through holes 39 also serve to cool the pistons. If a medium flows from the suction chamber 46 through the through bores, the respective piston 19 or 20 is cooled by this medium sucked in. In FIGS. 4 and 6 it can also be seen that between the pistons 19 and 20 and its associated cylinder walls 26 to 28, provided that the pistons 19 and 20 are in their end positions, there is no so-called harmful space. This means that the piston is in its end position at a very short distance from the respective cylinder wall. This ensures that the conveyed medium is completely pushed out of the conveying device 1 or during the suction process a volume of a medium is sucked in which corresponds to the volume of the space which is formed between an end face of the piston and the opposite cylinder wall. On the one hand, this improves the efficiency of the conveyor. On the other hand, high pressures can be generated because the medium is completely expelled from the cylinder chamber. In particular, the piston component 18 is driven in such a way that when the drive shaft is rotated 90 °, the pistons 19 and 20 each pass half the piston travel. Since the pistons 19 and 20 are fixedly attached to the middle part 22, a constant amount of a medium is conveyed each time the pistons 19 and 20 are moved back and forth. A sinusoidal drive is therefore provided here, as a result of which the conveyor device can run smoothly.

Since the pistons 19 and 20 require no lubrication in relation to the cylinder 14, the delivery device 1 can be used particularly advantageously for liquids without self-lubrication, such as gasoline, which is known to have essentially no lubrication properties.

If large volumes are to be delivered, it is also possible to design the pistons 19 and / or 20 and the associated cylinder walls to run obliquely. This means that when the piston is viewed from above, it has a parallelogram or diamond-shaped contour. The end faces of the piston are thus enlarged, so that there are larger through bores in cross section and thus larger check valves can be used.

In connection with FIG. 3, it should also be mentioned that it is also possible to drive the drive, consisting of crank disk 5, fork piece 8 and block piece 11, by a known crank drive, as used, for example, in the case of a windshield wiper drive. is used to replace. This makes it possible to drive a plurality of conveying devices 1 via the drive shaft 4, in which case it is preferably provided that only one crank drive is provided for all conveying devices, the conveying devices being connected to one another via a push rod. It can also be provided that at least two piston / cylinder units 3 are arranged one above the other. They are driven jointly via the drive shaft 4. For this purpose, it is provided that the piston shaft 12 of the two piston / cylinder units 3 is designed to be continuous. A piston shaft 12 is therefore provided, on which two piston components are arranged one above the other.

Finally, it should be noted that it is also easily possible to operate the conveyor 1 as a motor. It is preferably provided that the cylinder spaces 32 and 33 each comprise an ignition device, so that an internal combustion engine is formed, the driving force generated can be tapped off on the drive shaft 4.

In an exemplary embodiment of the conveying device, not shown in the figures, the medium to be conveyed is sucked into the cylinder spaces 32, 33 with a corresponding piston movement via at least one medium inlet opening in each case. The medium inlet openings can either be made in the pot-shaped lower part 15 of the cylinder 14 or in the cylinder cover 16 and open into the respective cylinder space. Furthermore, at least one medium outlet opening is assigned to each cylinder chamber, the medium outlet openings likewise are arranged either in the lower part 15 or in the cylinder cover 16 of the cylinder 14. When using the conveyor in pump or motor operation, a check valve is provided in each of the medium inlet and outlet openings in order to determine the direction of flow of the medium in one direction. The arrangement of the medium inlet and outlet openings in the side walls of the cylinder, i.e. in the lower part and in the cylinder cover, is particularly advantageous when using the conveying device described in FIGS. 1 to 9 in a modified form as an internal combustion engine, since valves can be dispensed with because here the piston clears the inlet and outlet opening (s) in the cylinder cover or in the lower part of the cylinder during its back and forth movement.

In all exemplary embodiments of the conveying device, the respective outlet opening through which the medium is expressed from the cylinder space by a corresponding piston movement can be connected to a pressure line leading directly to the consumer. In this embodiment variant, an ejection chamber 47 described with reference to FIGS. 4 to 9, which is arranged inside the cylinder 14, is dispensed with.

All embodiments of the conveyor device have in common that due to the extremely small distances between the side surface of the respective piston and the inner wall of the cylinder and between the outer periphery of the central part, to which the at least one piston is connected, and the inside 30 of the respective cylinder wall 25 to 28 a seal is created without the need to use separate sealants. The precise movement of the piston with the aid of the precision bearing 17 can ensure that the piston or the pistons do not touch the inner wall of the cylinder and / or the inside of the respective cylinder wall during operation of the conveying device, so that lubrication of these areas can be dispensed with .

It is particularly advantageous in the case of a conveying device described with the aid of the preceding figures that no sliding friction arises and thus almost only the pure compression work has to be performed to compress a medium. As a result, less energy is consumed, so that less heat is generated during the operation of the conveying device than in comparable conveying devices known from the prior art. Because the piston or the pistons do not touch the cylinder wall, there is also no so-called breakaway torque. The torque required to start the conveyor from a standstill is therefore only low in comparison to the known conveyor devices. It is also advantageous that the distance between the pistons and the cylinder wall prevents contact corrosion between the pistons and the cylinder wall, even after the conveyor has been idle for a long time. It is also advantageous that the medium is conveyed by the piston and only one valve has to be installed per surface, so that large valve surfaces can be realized, which in turn reduces the flow losses of the conveying device can. Since the direction of flow of the medium in the working space in which the respective piston is moving does not have to be reversed, this also has an advantageous effect on resonance charging.

FIG. 10 shows a side view of an exemplary embodiment of a device for driving through a medium, hereinafter referred to as internal combustion engine 101, which has a housing 102 and a working unit 103. An output shaft 104 is rotatably mounted in the housing 102, on which a torque generated by the working unit 103 can be tapped. At the free end of the output shaft 104, a crank disk 105 is connected to the output shaft in a rotationally fixed manner. A fork piece 107 is pivotally mounted in a recessed recess, not shown in FIG. 10, eccentrically to the longitudinal center axis of the crank disk 105 or the output shaft 104, the fork arms 109 of which are pivotally connected to a block piece 111 about an axis 110 running horizontally in FIG. The block piece 111 is rotatably connected to a piston shaft 112.

The working unit 103 comprises a pot-shaped lower part 113 and a cover 115 which is designed as a circular plate which is screwed to the lower part 113 using suitable fastening means, for example with machine screws. A precision bearing 117 is arranged in the housing 102 and rotates the piston shaft 112 exactly and also in the exact axial position. In the interior of the circular hollow cylindrical lower part 113 of the working unit 103 are a pressure plate 119, a Housing block 121 and a connecting plate 123 are arranged which are stacked on top of one another, the housing block 121 being arranged between the pressure plate 119 arranged on the bottom of the pot-shaped lower part 113 and the connecting plate 123.

FIG. 11 shows a plan view of a schematic diagram of an exemplary embodiment of a housing block 121, in which an edge-open recess 125 is made, in which a piston component 127 is rotatably guided about the longitudinal central axis of the piston shaft 112 along a partial circular movement. The piston component 127, which is non-rotatably connected to the piston shaft 112, has a first piston 129 and a second piston 131, both of which are offset radially outward from the pivot point 133 of the piston component 127. The fulcrum 133 lies on the axis of rotation (longitudinal center axis) of the piston shaft 112. The piston component 127 has a circular middle part 135, from which the first and the second pistons 129, 131 extend radially outward in a wing-like manner, the respective pistons 129, 131 to extends to a side wall 137 of the recess 125. The side wall 137 is curved, the curvature corresponding to that of an imaginary circle with the pivot point 133 as the center and the radius r.

The side surface 139 of the respective piston 129, 131 is designed in accordance with the inner curvature of the side wall 137 and is therefore convexly curved. The side wall 137 of the recess 125 faces the side surface 139 of the piston without contact with extremely little play, such that there quasi a seal is created. Because of the very thin gap between the side surface 124 of the piston 129, 131 and the side wall 137 of the recess 125 and the relatively long length of the side surface 139, as seen in the direction of movement of the pistons, separate sealing means, for example sealing washers, rings or the like, are not here required. The side walls 141 of the recess 125, which face the central part 135 of the piston component 127 at an extremely short distance, are adapted to the outer periphery 143 of the central part 135, so that movement of the piston component 127 about the pivot point 133 can occur, but between the mentioned Surfaces a seal is formed. Due to the very small gap height, additional seals or sealants can also be dispensed with here.

As can be seen from FIG. 11, the regions of the recess 125 in which the pistons 129 and 131 are moved back and forth are designed in the manner of a circular cutout. These working areas in the form of a circular section, in each of which one of the pistons 129, 131 is located, are divided by the pistons 129, 131 into a suction chamber 144 or 146 and into a combustion chamber 145 or 147, respectively. When the piston component 127 moves clockwise about the pivot point 133, the combustion chamber 145 is reduced by a displacement of the piston 129 and at the same time the suction chamber 144 is enlarged, while the combustion chamber 147 is enlarged by the displacement of the piston 131 and the suction chamber interacting with the combustion chamber 147 146 can be reduced. In the base 149 of the recess 125, an intake duct 151 and an exhaust duct 153 leading to the exhaust pipe are each introduced in the area of the working spaces for the pistons 129, 131. The intake channels 151 are circular in their mouth area and the outlet channels 153 are square. Of course, their design is variable; for example, the outlet ducts 153 can be kidney-shaped in their area opening into the combustion chambers 145, 147.

The internal combustion engine 101 also has an ignition device 155, which in each case comprises a spark plug 157 for each of the combustion chambers 145, 147. The spark plugs 157 arranged in the blind bores 159 in the housing block 121 are screwed into threaded bores and protrude into the respective combustion chamber 145 or 147, so that a compressed fuel-air mixture located in the combustion chambers 15, 147 can be ignited. The structure and function of an ignition device for an internal combustion engine is generally known, so that its structure is not described in detail.

FIG. 14 shows a side view of the connection plate 123 described with reference to FIG. 10, in which intake ducts 151 'and outlet ducts 153' are introduced, which open into an intake chamber 161 or discharge chamber 163 shown with a broken line. The suction chamber 161 is provided with a fuel or fuel-air mixture supply line, not shown, and the exhaust valve 163 comes with an exhaust pipe (exhaust). connected. In the assembled state of the working unit 103, the connection plate 123 rests with its flat contact surface 165 on the flat rear side of the housing block 121, i.e. on the side of the housing block 121 opposite the recess 125, one of the outlet channels 151 'in the connection plate 123 with the respective suction channel 151 opening into the suction chamber 144 or 146. In the intake channels 151 and / or intake channels 151 'there is in each case a check valve, not shown in the figures, which allows passage from the intake chamber 161 into the intake chamber 144 or 146 and a backflow of the fuel-air mixture drawn from the intake chamber 161 prevented from the suction chamber 144 or 146 into the suction chamber 161. Alternatively, it is of course also possible to design the internal combustion engine so that no valves, in particular check valves, are necessary.

FIG. 13 shows a plan view of an exemplary embodiment of a pressure plate 119 of the working unit 103, which is formed by a flat plate. A through hole 167 is provided in the center of the pressure plate 119, through which the piston shaft 112 is inserted. In the contact surface 168 of the pressure plate 119, with which it rests in the assembled state of the working unit 103 on the front side of the housing block 121 which has the recess 125, two overflow channels 169 and 171, respectively, are arranged radially offset to the center of the pressure plate 119, depending on their function will be discussed in more detail below. The arrangement and configuration of the overflow channels 169, 171 which are open at the edge in this exemplary embodiment and which are formed here by elongated depressions can be varied. In a further embodiment variant, not shown, the overflow channels 169, 171 are designed as through openings which at least partially penetrate the pressure plate 119. In the assembled state of the pressure plate 119, the through openings must be closed on their side facing away from the front of the housing block. For this purpose, for example, a cover plate can be attached to the pressure plate, for example screwed on.

FIG. 12 shows a plan view of the exemplary embodiment of the housing block 121 described with reference to FIG. 11. The piston component 127 is arranged here in an end position, which it assumes by rotating clockwise around the pivot point 133. In the position of the piston component 127 shown in FIG. 11, it is in its other end position, which it assumes by rotating it counterclockwise.

In this exemplary embodiment, the internal combustion engine 101 described with reference to FIGS. 10 to 14 is a two-stroke internal combustion engine for, for example, gasoline and / or diesel operation. Of course, the internal combustion engine 101 can also be operated with other fuels, for example methane. When the internal combustion engine 101 is in operation, the piston shaft 112 and thus the block piece 111 attached to it in a rotationally fixed manner is caused by an oscillating back and forth movement of the piston part 127 vibrated. Characterized the fork piece 107 is moved in a corresponding manner, whereby a rotation of the crank disk 105 is initiated. The torque transmitted in the process can, as said, be taken off on the rotating output shaft 104. In a further embodiment of the internal combustion engine 101, not shown, it is provided that it operates in four-stroke mode and accordingly has a correspondingly modified construction.

The two work cycles of the two-stroke internal combustion engine are explained in more detail below: starting from the position of the piston component 127 shown in FIG. 11, the first cycle of the piston 129 begins by an oscillating movement of the piston component 127 about the pivot point 133 in a clockwise direction. In this case, a fuel-air mixture is drawn from the suction chamber 161 into the suction chamber 144 assigned to the combustion chamber 145 via the suction channels 151, 151 '. The fuel-air mixture located in the combustion chamber 145 is compressed from the moment in which the piston 129 has passed over the outlet channel 153 and has thus been covered, that is to say closed. After the piston 129 has reached a certain position, for example the position shown in FIG. 12, the fuel-air mixture in the combustion chamber 145 is ignited with the aid of the ignition device 155. The further movement of the piston 129, that is to say the second cycle, then takes place in the reverse manner, that is to say the piston 129 now moves counterclockwise back into the position shown in FIG. 11. Due to the arrangement of the outlet duct 153 and the design 12 of the overflow channel 169 in the pressure plate 119, the outlet channel 153 is first opened before the fuel-air mixture compressed in the suction chamber 144 by pivoting the piston 129 counterclockwise through the overflow channel 169 can get into the combustion chamber 145. After the piston 129 has passed over the right end region of the overflow duct 169 with the side surface facing the combustion chamber 145, the mixture which has been precompressed in the suction chamber 144 flows through the overflow duct 169 into the combustion chamber 145, which is flushed thereby, that is to say which is still in the combustion chamber Exhaust gases located in 145 are preferably pushed out completely, or at least largely, through outlet duct 153. Corresponding processes take place in the piston 131, the fuel-air mixture being sucked into the suction chamber 145 by a piston movement due to the arrangement and configuration of the intake and outlet channels in the housing block 121, while the piston 131 simultaneously detects the fuel located in the combustion chamber 147 -Air mixture compressed.

It is clear from everything that the internal combustion engine 101 can also comprise only one piston or more than two pistons, for example three or four pistons. It remains to be noted that the pistons 129, 131 in their end positions shown in FIGS. 11 and 12 do not rest on a side surface of the recess 25, but are preferably located at a very short distance from the latter. In the exemplary embodiment of internal combustion engine 101 described with reference to the figures, the drive of piston component 127 is designed in such a way that output shaft 104 rotates through 90 ° when pistons 129, 131 each pass half the piston path. A sinusoidal drive is therefore provided here, as a result of which the internal combustion engine can run smoothly.

In connection with FIG. 10, it should also be mentioned that it is also possible to replace the output, consisting of block piece 111, fork piece 107 and crank disk 105, by a known crank drive, as is used, for example, in a windshield wiper drive. It can also be provided that at least two working units 103 are arranged one above the other. They are driven together via the output shaft 104. For this purpose, it is provided that the piston shaft 112 of the two working units 103 is designed to be continuous. Thus, only one piston shaft 112 is provided, on which two piston components, each having at least one piston, are arranged one above the other.

The internal combustion engine can advantageously be used in combination with a delivery device for a liquid or gaseous medium. In one embodiment variant, it is provided that the conveying device comprises at least one piston component which can be pivoted about an axis and has at least one piston attached to it, the piston component of the conveying device being connected in a rotationally fixed manner to the piston shaft 112 of the internal combustion engine. The internal combustion engine and conveyor unit formed is characterized by a simple, compact and inexpensive structure. It is also advantageous that the swiveling movement of the piston shaft 112 generated by the internal combustion engine does not have to be converted into a rotary movement in order to drive the conveying device, but that the drive torque introduced into the piston shaft 112 can thus be used directly by us with little loss. In this embodiment variant, the output shaft 104 shown in FIG. 10 is preferably only required as a pacemaker and as a stroke limiter for the piston component of the internal combustion engine and that of the delivery device. Because the internal combustion engine and the conveying device are arranged to the left and right of the block piece 111 and the crank disk 105, the influence of the heat radiated by both devices on the remaining parts is reduced to an innocuous degree.

In summary, it should be noted that the defined guidance of the piston movement outside the combustion chamber with the aid of at least one bearing enables the movement path of the at least one piston of the internal combustion engine to be guided so precisely that contact with the piston with one of the walls delimiting the combustion chamber can be ruled out. Sealing the combustion chamber, in particular the gap between the side surface 139 of the piston and the side wall 137 (combustion chamber wall) of the respective combustion chamber, is possible solely because of the small distance between these two surfaces. This means that there are no separate seals such as those known from the prior art Internal combustion engines are needed. Furthermore, there is no need to lubricate the piston since it does not slide on the combustion chamber wall. Another advantage that results from the fact that the piston (s) does not touch / touch the combustion chamber wall is that the design of the overflow, suction and exhaust ducts or slots is practically arbitrary. The internal combustion engine 1 is also characterized by a simple and therefore inexpensive construction. Due to the configuration described above, sliding friction between the piston or pistons of the internal combustion engine and the combustion chamber wall is avoided, so that the internal combustion engine can be started with low forces, preferably even in the cold.

Claims

Expectations

1. Device for the conveyance of a liquid or gaseous medium or for driving through a medium with a piston / cylinder unit, characterized in that the movement of the piston is guided by means of a bearing (precision bearing) and that the bearing (precision bearing) is outside of the cylinder (cylinder chamber, combustion chamber).

2. Device according to claim 1, characterized in that the medium is sucked in by means of a piston movement and is conveyed by means of opposite piston movement and due to the function of a valve device.

3. Device according to one of the preceding claims, characterized in that the piston (19, 20) performs a partial circular movement about a pivot point (21).

4. Device according to one of the preceding claims, characterized in that the piston (19, 20) is formed on a rotating part (piston component 18).

5. Device according to one of the preceding claims, characterized in that the rotating part (piston component 18) is guided by the bearing (precision bearing 17) and that the piston (19, 20) is radially offset from the pivot point (21).

6. Device according to one of the preceding claims, characterized in that the piston (19, 20) performs an oscillating movement.

7. Device according to one of the preceding claims, characterized in that a first end face of the piston (19, 20) facing first cylinder wall (25 to 28) is penetrated by at least one check valve (35 to 38, 51 to 58).

8. Device according to one of the preceding claims, characterized in that a first end face of the piston (19, 20) facing first cylinder wall (25 to 28) of at least two check valves (35 to 38, 51 to 58) is interspersed with each other have opposite pass directions.

9. Device according to one of the preceding claims, characterized in that the piston (19, 20) is penetrated by at least one check valve (40 to 43).

10. Device according to one of the preceding claims, characterized in that one of the other, second end face of the piston (19, 20) facing second cylinder wall (25 to 28) is penetrated by at least one check valve (35 to 38, 51 to 58).

11. Device according to one of the preceding claims, characterized in that the distance between the side surface (24) of the piston (19, 20) and the inner wall (inside (23)) of the cylinder (14), especially in the operation of the device, is extremely small.

12. Device according to one of the preceding claims, characterized in that the piston (19, 20) is guided without a seal relative to the cylinder inner wall in the cylinder chamber (32, 33).

13. The device, in particular according to one of the preceding claims, in particular an internal combustion engine, with at least one combustion chamber and at least one piston, the combustion chamber being reduced by a piston movement and the combustion chamber being enlarged by an opposite piston movement.

14. The device according to one or more of the preceding claims, characterized in that the piston is guided without a seal relative to the combustion chamber wall (side wall 137) in the combustion chamber (145, 147).

15. The device according to one or more of the preceding claims, characterized in that the side surface (139) of the piston (129, 131) and the combustion chamber wall (side wall 137) face each other at an extremely short distance.

16. Device according to one of the preceding claims, characterized in that the piston (129, 131) performs a partial circular movement about a pivot point (133).

17. Device according to one of the preceding claims, characterized in that the piston (129, 131) on a rotating part (middle part 135), preferably in one piece.

18. Device according to one of the preceding claims, characterized in that the rotating part (middle part 135) of the bearing (precision bearing 117) is guided and that the piston (129, 131) is located radially to the pivot point (133).

19. Device according to one of the preceding claims, characterized in that the piston (129, 131) performs an oscillating movement.