Operating engine

Abstract

The present invention relates to a working engine that comprises a working volume or plurality of working volumes. The working volume(s) are each assigned one or more inlet valves and one or more outlet valves. The inlet valve(s) are connected to a supply line arrangement that supplies a medium. The inlet valve(s) are arranged so that when an inlet valve is open, the medium is supplied to the working volume assigned to the inlet valve. The outlet valve(s) are connected to a discharge line arrangement. In the working phase of increasing the working volume(s), the inlet valve(s) associated with the working volume(s) are open and the outlet valve(s) associated with the working volume(s) are closed. In the working phase of reducing the working volume(s), the outlet valve(s) associated with the working volume(s) are open and the inlet valve(s) associated with the working volume(s) are closed.

Description

The present invention relates to an operating engine according to the general term of Claim 1.

SUMMARY OF THE INVENTION

The fundamental design of this type of operating engine is known as a reciprocating machine. The mode of action of these known operating engines is based on a fuel-air mixture being ignited at some point (at the beginning of a work cycle). The drive energy in the operating engine results from the energy that is released in the combustion of the fuel-air mixture. The reciprocating machines are known as 2-stroke or 4-stroke operating engines. The rotary piston engines are known as Wankel engines.

This means that the operating engine has one or several work volumes. The work volume or work volumes of the operating engine are allocated one or several inlet valves each as well as one or several outlet valves.

The one or several inlet valves are arranged in such a way that they are connected to a supply line arrangement, into which a pressurised medium is supplied. The one or several inlet valves are also arranged in such a way that the pressurised medium is fed to the respective work volume that is allocated to the respective inlet valve when the inlet valve is open.

The one or several outlet valves are connected to a discharge line arrangement, through which the medium is discharged. The one or several outlet valves are also arranged in such a way that the medium is fed away through the discharge line arrangement from the work volume allocated to the respective outlet valve.

The following describes the functioning of an operating engine based on the example of a 4-stroke operating engine with a reciprocating piston. In the case of state-of-the-art operating engines, the respective inlet valve is not opened in each work phase to increase the work volume.

In the state of the art (for a 4-stroke operating engine) a so-called intake cycle takes place. The inlet valve on the work volume is open during this intake cycle. The work volume fills with the medium.

Thereafter follows a work cycle with a reduction of the work volume. In the state-of-the-art operating engine both the inlet valve and the outlet valve on the work volume are closed at this time. The medium in the work volume is compressed. The mixture in the work volume is ignited shortly before the upper dead centre is reached. This presses the piston downwards in the following work cycle to increase of the work volume. In this work cycle both the inlet valve and the outlet valve are closed. in the work cycle that then follows, the (combusted) mixture is pressed out of the work volume through the open outlet valve. Another intake cycle takes place subsequently

A pressurised gas engine is known from DE 10 2008 010 359 A1. Gas can flow into a cylinder from a pressurised container through an inlet valve and a quick-action valve and move a piston. The gas can flow out of cylinder 3 through an outlet valve 10.

A cylinder with a double piston is known from US 2012 0 096 845 A1, in which the cylinder is divided into two chambers.

According to the present invention the drive energy of the operating engine results from the pressure with which the medium flows through the open inlet valve or open inlet valves that are allocated to the open inlet valve or open inlet valves.

The present invention is a reciprocating piston engine with double cylinders with double pistons that move inside them, whereby a secondary volume of the double cylinder is connected to the work volume or one of the work volumes of the operating engine, and a primary volume of the cylinder includes the inlet valve or inlet valves and the outlet valve or outlet valves.

The double piston is constructed in such a way that the piston rod and the piston itself are hollow inside. The piston rod is open at the end where the piston is not attached.

The piston is sealed against the cylinder wall of the double cylinder. The piston rod is sealed against the wall at the end facing away from the piston. The pressurised medium flows through this into the inside of the double piston when the inlet valved are open. The medium is thus pressed out of the inside of the piston and piston rod when the outlet valves are open. There is at least one air vent or ventilation opening in the volume of the double piston, which is enlarged through the movement of the double piston when the inlet valves are open.

The inside of the piston and the piston rod are thus part of the primary volume of the double cylinder in this embodiment.

If the double piston is moved when the inlet valves are open, then air is taken in through these ventilation openings so that no negative pressure is created against which the double piston needs to be moved. When the outlet valves are open the movement of the double piston displaces the air again that was previously taken in, without the double piston having to compress this air during its movement.

A transmission ratio can be set when operating the 30 operating engine using the size of the volumes of the inside of the piston and the piston rod in comparison to the secondary volume of the double cylinder, which is equivalent to the working travel of the double piston.

In the work phase of increasing the work volume for the respective work volumes the inlet valve or inlet valves allocated to the work volume or respective work volumes are open. The outlet valve or outlet valves allocated to the work volume or respective work volumes are closed at this time. In the present invention this occurs in each work cycle with an increase in work volume.

In the work cycle of the reduction of the work volume or the respective work volumes the outlet valve or outlet valves allocated to the work volume or the respective work volumes are open. The inlet valve or inlet valves allocated to the work volume or respective work volumes are then closed. This takes place in the present invention in each work cycle with a reduction in work volume.

It is advantageous that this makes it possible to use the energy “contained” in the flow when using a flowing medium (for example with a body of water) without the need for combustion. This means that the operating materials are available at a low price, or even free of charge.

The operating engine continues to deliver the performance using the present invention without producing exhaust gases from combustion.

In the embodiment according to Claim 2 the operating engine for the medium has a dual circuit arrangement. The dual circuit arrangement is created by having at least one cylinder with a double piston. The secondary volume of the cylinder with the double piston is connected to the work volume or to one of the work volumes of the operating engine. The primary volume of the cylinder with the double piston includes both the inlet valve or inlet valves and the outlet valve or outlet valves. It is advantageous if each work volume has one such cylinder.

The dual circuit arrangement is advantageous as there is no exchange of flowing material in the work volume of the operating engine. The exchange of medium in the work volumes of the operating engine takes place with the secondary volume of the cylinder. It is advantageous that this avoids contamination of the operating engine as the medium flowing there is inert. The exchange with the flowing “foreign” medium takes place in the primary volume of the respective cylinder. It proves to involve substantially less effort to exchange the cylinder in the event of contamination or damage than to undertake repairs or cleaning work on the operating engine.

The opening and closing of the inlet and outlet valves can be carried out with a camshaft or through electronic control of the inlet and outlet valves. The opening and closing of the inlet and outlet valves is synchronised with the work phases of the work volumes (either increasing the work volume or decreasing the work volume).

DESCRIPTION OF THE DRAWINGS

One embodiment of the invention is shown in the figure. It shows:

FIG. 1: A sectional view of a reciprocating piston in a known operating engine in the work phase of increasing the work volume,

FIG. 2: a sectional view of a reciprocating piston in a known operating engine in the work phase of the reduction of the work volume,

FIG. 3: a sectional view of a reciprocating piston in a known operating engine in a dual circuit arrangement of the operating engine,

FIG. 4: a sectional view of a reciprocating piston in a known rotary piston machine,

FIG. 5: a schematic representation of two co-operating cylinders with reciprocating pistons acting on a connecting rod,

FIG. 6: a schematic representation of ten co-operating cylinders that are co-operating in two groups of five cylinders each with a double piston for each group,

FIG. 7: the arrangement according to FIG. 6 in a top view from above,

FIG. 8: a schematic representation of an arrangement of ten co-operating cylinders that are co-operating in two groups of five cylinders each with a different construction of the double cylinder,

FIG. 9: the arrangement according to FIG. 8 in a top view from above.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 shows a sectional view of a cylinder 1 of an operating engine in the work phase of increasing the work volume. Piston 2 is shown (reciprocating piston) with the direction of movement (arrow 3) of piston 2. It can be seen that the inlet valve 4 is open. The outlet valve 5 is closed.

FIG. 2 shows a sectional view of cylinder 1 according to the presentation in FIG. 1, but in the work phase of reducing the work volume. This is shown by arrow 201. It can be seen that the outlet valve 5 is opened in this work phase. Inlet valve 4 is closed.

FIG. 3 shows a sectional view of a cylinder 1 of an in a dual circuit arrangement of the medium for the operating engine. A double piston cylinder 301 can be seen. The double piston 302 limits a secondary volume 303 and a primary volume 304 in the double piston cylinder 301. The secondary volume 303 is connected to the work volume of cylinder 1.

Arrow 308 shows that reciprocating piston 2 moves upwards. This thus reduces the work volume of cylinder 1. This thus increases the secondary volume 303 of the double piston cylinder 301. An inlet valve 306 and an outlet valve 307 is allocated to the primary volume 304 of the double piston cylinder 301. In the work phase represented here, the outlet valve 307 is opened and the inlet valve 306 is closed. This presses the medium out of the primary volume 304 of the double piston cylinder.

In a work phase of the increase of the work volume of cylinder 1 the inlet valve 306 is opened and the outlet valve 307 closed. The secondary volume 303 is reduced by the medium flowing into the primary volume 304. This causes the medium in the secondary volume 303 to flow into the work volume of cylinder 1 and drives this.

FIG. 4 shows a sectional view of a rotary piston operating engine 401. The inlet valves 402 and 403 and outlet valves 404 and 405 can be seen. The inlet valves 402 and 403 and the outlet valves 404 and 405 are opened and closed according to the current position of the rotary piston in such a way that the respective inlet valve is open, and the corresponding outlet valve closed in a phase of increasing the respective work volume. The corresponding outlet valve is open, and the corresponding inlet valve closed in a phase of reducing the respective work volume.

In the representation in FIG. 4 it can be seen that there is a further arrangement of inlet and outlet valves at the position of the rotary piston operating engine where the spark plugs are usually located. This fills or empties the work volumes so that the rotary piston is driven by the flow pressure of the medium.

FIG. 5 is a schematic representation of two co-operating cylinders 501 and 502 with reciprocating pistons acting on a connecting rod. The two cylinders work as a dual circuit system with one double cylinder 503 and 504 each. The main lines of the double cylinders 503 and 504 can be seen (labelled with the reference numbers 503 and 504), which lead to the individual cylinders.

The double cylinder 503 has a double piston 505 which is shown in the position at the stop at which the primary volume is minimal. The medium in the primary volume of this double cylinder 503 is pressed out completely through the valve 509.

This valve 509 is located at the position where the primary volume of this double cylinder 503 is connected with the main line, through which the medium is connected to cylinder 501 as well as further cylinders that are synchronised with cylinder 501 with regard to the power stroke.

The double cylinder 504 has a double piston 507, which is located at the stop in the position shown, where the primary volume is at a maximum. The primary volume of this double cylinder 504 is completely filled with the pressurised medium via the valve 510. This valve 510 is located in the position in which the primary volume of this double cylinder 504 is connected to the supply line. The secondary volume 508 of the double cylinder 504 is connected with the main line, via which the medium is connected to the cylinder 502 and with further cylinders that are simultaneously synchronised with the cylinder 502 with respect to the work cycle.

The cylinders 501 and 502 are arranged in relation to each other according to the principle of a boxer engine, so that the work cycles of these cylinders 501 and 502 are simultaneously synchronised with one another.

In FIG. 5 it can be seen that in place of separate 2/2 valves for the inlet valves and the outlet valves, 3/2 valves can also be provided (509 and 510), which alternately connect either the supply line arrangement or the discharge line arrangement to the primary volume of the respective double cylinder 503, 504.

FIG. 6 shows a schematic representation of ten co-operating cylinders 601, 602, 603, 604, 605 and 606, 607, 608, 609, 610, which work together in two groups (601, 602, 603, 604, 605==Group 1, and 606, 607, 608, 609, 610==Group 2) of five cylinders each with one double piston per group. The double cylinder 611 is allocated to Group 1 and the double cylinder 612 to Group 2.

The cylinders 601, 602, 603, 604, 605 in Group 1 are simultaneously synchronised with one another. The cylinders 606, 607, 608, 609, 610 in Group 2 are also simultaneously synchronised with one another. The cylinders in Groups 1 and 2 are synchronised with one another in opposite directions.

In the embodiment example shown in FIG. 6 the primary volume of the double cylinder 612 is being connected with the supply line. The piston on this double cylinder 612 is just at the point when the direction of movement of the double piston changes from the direction to reduce the primary volume to the direction to increase the primary volume. Correspondingly, the primary volume of the double cylinder 611 is just connected to the discharge line.

FIG. 7 shows the arrangement according to FIG. 6 in a top view from above. The representation of FIG. 7 aims to explain the double piston that is used in the double cylinders in FIGS. 5 to 9. This piston is constructed in such a way that the piston rod and the piston itself are hollow. The piston rod is open at the end to which the piston is not attached. It can be seen that the piston is sealed against the cylinder wall of the double cylinder. Also, the piston rod is sealed against the wall in the area of the end facing away from the piston.

The pressurised medium thus flows into the inside of the double piston when the inlet valves are opened. If the outlet valves are opened, this medium is pressed from the inside of the piston and the piston rod. The inside of the piston and the piston rod are thus part of the primary volume of the double cylinder in this embodiment.

It can be seen that there is at least one air vent or ventilation opening in the volume of the double piston that exists “behind” the double piston through the movement of the double piston when the inlet valves are open. If the double piston is moved when the inlet valves are open, then air is taken in through these ventilation openings, so that no negative pressure is created, against which the double piston needs to be moved. When the outlet valves are opened the movement of the double piston causes the air that was taken in previously to be displaced from the double cylinder without the double piston needing to compress this air during its movement.

A transmission ratio can be set when operating the operating engine via the size of the volumes of the inside of the piston and the piston rod in comparison to the secondary volume of the double cylinder, which is equivalent to the working travel of the double piston.

In an embodiment of the double cylinder and the double piston in accordance with FIG. 3 the double piston is solid. The primary volume of this double cylinder consists of the double piston being displaced “into the secondary volume”. This double cylinder has a transmission ratio of 1:1.

In principle, the use of a double cylinder as shown in FIG. 3 is possible in all embodiments, as well as in accordance with the explanations in connection with FIG. 7.

FIG. 8 shows a schematic representation of an arrangement of ten co-operating cylinders 801, 802, 803, 804, 805 and 806, 807, 808, 809, 810, in two groups (801, 802, 803, 804, 805==Group 1; 806, 807, 808, 809, 810==Group 2) with five cylinders with one double piston per group, with a different construction compared to the representation in FIG. 6.

The double pistons 812 and 813 are allocated to the main line 811, which is connected to the cylinders 801, 802, 803, 804 and 805.

The double pistons 814 and 815 are connected to a main line 901, which is connected to the cylinders 806, 807, 808, 809 and 810. The main line 901 is hidden by main line 811 in the representation of FIG. 8.

FIG. 9 shows the arrangement according to FIG. 8 in a top view from above. In this representation the main line 901 can be seen.

Claims

1. (canceled)

2. (canceled)

3. (canceled)

4. (canceled)

5. (canceled)

6. (canceled)

7. (canceled)

8. (canceled)

9. (canceled)

10. (canceled)

11. A working engine comprising: at least one working volume;double cylinders having a movable double piston therein;at least one inlet valve associated with the at least one working volume; andat least one outlet valve associated with the at least one working volume;wherein the at least one inlet valve is connected to a supply line arrangement that a medium is fed therethrough;wherein the at least one inlet valve is arranged such that when the at least one inlet valve is open, the medium is supplied to the at least one working volume;wherein the at least one outlet valve comprises a respective discharge line arrangement that the medium is dischargeable therethrough;wherein the outlet valves are arranged such that when the outlet valves are open the medium from the at least one working volume is discharged via the discharge line arrangement;wherein when the at least one inlet valve and the at least one outlet valve are in a first working phase to increase the at least one working volume, the at least one inlet valve is open and the at least one outlet valve is closed;wherein when the at least one inlet valve and the at least one outlet valve are in a second working phase to reduce the at least one working volume, the at least one outlet valve is open and the at least one inlet valve is closed;wherein a secondary volume of the double cylinders is connected to the at least one working volume, and a primary volume of the double cylinders include the at least one inlet valve and the at least one outlet valve;wherein a drive energy results from a pressure caused by the medium flowing into the at least one working volume via the at least one inlet;wherein the double piston includes a piston rod that has an opening at an end thereof;wherein the double piston and the piston rod are hollow;wherein the double piston is sealed against a cylinder wall of the double cylinders;wherein the piston rod is sealed against the cylinder wall at an end of the piston rod facing away from the double piston;wherein the medium flows into the double piston when the at least one inlet valve is open;wherein the medium is pressed out of the double piston and the piston rod when the at least one outlet valve is open;wherein the double piston comprises at least one volume that is increased when the at least one inlet valve is open via movement of the double piston; andwherein the at least one volume of the double piston comprises at least one air ventilation opening.

12. The working engine according to claim 1, further comprising a dual-circuit arrangement that comprises at least one secondary cylinder having a respective secondary double piston; wherein a secondary volume of the at least one secondary cylinder is connected to the at least one working volume; and wherein a primary volume of the at least one secondary cylinder includes at least one secondary inlet valve and at least one secondary outlet valve.