CN212690186U

CN212690186U - Engine

Info

Publication number: CN212690186U
Application number: CN202020939379.3U
Authority: CN
Inventors: 靳北彪
Original assignee: Entropy Zero Technology Logic Engineering Group Co Ltd
Current assignee: Entropy Zero Technology Logic Engineering Group Co Ltd
Priority date: 2020-04-19
Filing date: 2020-05-28
Publication date: 2021-03-12
Anticipated expiration: 2030-05-28
Also published as: CN111664000A

Abstract

The utility model discloses an engine, set up piston A on reciprocal active cell A₁And piston A₂A piston B is arranged on the reciprocating rotor B₁And piston B₂A piston C is arranged on the reciprocating mover C₁And piston C₂A piston D is arranged on the reciprocating mover D₁And a piston D₂Piston A₁Is arranged in a cylinder A₁Inner, piston A₂Is arranged in a cylinder A₂Inner, piston B₁Is arranged in a cylinder B₁Inner, piston B₂Is arranged in a cylinder B₂Inner and reciprocating rotor A via transmission gear AB andthe reciprocating rotor B is arranged in a linkage manner, the reciprocating rotor B is fixedly connected with the reciprocating rotor C, and the reciprocating rotor C is arranged in a linkage manner with the reciprocating rotor D through a transmission gear CD. The utility model discloses an engine can overcome traditional free piston engine atress unbalance effectively and bring the defect such as cost height, bulky, weight are big, vibration is big, and has good energy-concerving and environment-protective nature, fuel adaptability.

Description

Engine

Technical Field

The utility model relates to a heat energy and power field especially relate to an engine.

Background

The traditional free piston engine has the defects of strong working vibration, large noise and the like due to unbalanced stress caused by working, and the traditional free piston engine has the defects that a motor is used for driving a piston to complete power consumption processes such as a compression stroke and the like, so that the high requirements on the instantaneous power of the motor and the instantaneous power of a power supply are inevitably caused, and the problems of high manufacturing cost, large volume, large weight and the like are caused. If the engine with the motion system self-balancing function and the inertia energy storage and release mode of the motion system for solving the power consumption process of the piston can be invented, the free piston and the high-efficiency engine can be widely applied, and the energy-saving and environment-friendly performance and the fuel adaptability of the engine are improved. Therefore, a new engine needs to be invented.

SUMMERY OF THE UTILITY MODEL

In order to solve the above problem, the utility model provides a technical scheme as follows:

scheme 1: an engine comprises a cylinder A₁Cylinder A₂Cylinder B₁Cylinder B₂And a cylinder C₁And a cylinder C₂Cylinder D₁Cylinder D₂The reciprocating rotor A is provided with a piston A, a reciprocating rotor B, a reciprocating rotor C, a reciprocating rotor D, a transmission gear AB and a transmission gear CD₁And piston A₂A piston B is arranged on the reciprocating rotor B₁And piston B₂A piston C is arranged on the reciprocating mover C₁And piston C₂A piston D is arranged on the reciprocating mover D₁And a piston D₂Said piston A₁Is arranged at the cylinder A₁Inner, the piston A₂Is arranged at the cylinder A₂Inner, the piston B₁Is arranged in the cylinder B₁Inner, the piston B₂Is arranged in the cylinder B₂Inner, the piston C₁Is arranged in the cylinder C₁Inner, the piston C₂Is arranged in the cylinder C₂Inner, the piston D₁Is arranged in the cylinder D₁Inner, the piston D₂Is arranged in the cylinder D₂The reciprocating rotor A is in linkage with the reciprocating rotor B through the transmission gear AB, the reciprocating rotor B is fixedly connected with the reciprocating rotor C, the reciprocating rotor C is in linkage with the reciprocating rotor D through the transmission gear CD, and the cylinder A₁The cylinder A₂The cylinder B₁The cylinder B₂The cylinder C₁The cylinder C₂The cylinder D₁And the cylinder D₂Operating in a four-stroke mode of operation or in a two-stroke mode of operation.

Scheme 2: on the basis of the scheme 1, at least one of the transmission gear AB and the transmission gear CD is further selectively arranged in linkage with the rotational inertia body.

Scheme 3: on the basis of the scheme 2, the setting for enabling the rotary inertia of the rotary inertia body to be adjustable is further selected selectively.

Scheme 4: on the basis of the scheme 2, the rotary inertia body is further selectively arranged as the motor rotor or a part of the motor rotor.

Scheme 5: on the basis of the scheme 3, the rotary inertia body is further selectively arranged as the motor rotor or a part of the motor rotor.

Scheme 6: on the basis of any one of the aspects 1 to 5, the cylinder a is further selectively selected₁The cylinder A₂The cylinder B₁The cylinder B₂The cylinder C₁The cylinder C₂The cylinder D₁And the cylinder D₂An ignition device is arranged in the device.

Scheme 7: on the basis of the scheme 6, the ignition device is further selectively enabled to work in an differential ignition mode; or, the ignition device is enabled to work according to a full ignition mode; or, operating the ignition device in a full-point mode at a single-differential-time.

Scheme 8: on the basis of any one of the aspects 1 to 5 and 7, the cylinder a is further selectively selected₁The cylinder A₂The cylinder B₁The cylinder B₂The cylinder C₁The cylinder C₂The cylinder D₁And the cylinder D₂A fuel injection device is arranged in the fuel injection device.

Scheme 9: on the basis of the scheme 6, the cylinder A is further selectively selected₁The cylinder A₂The cylinder B₁The cylinder B₂The cylinder C₁The cylinder C₂The cylinder D₁And the cylinder D₂A fuel injection device is arranged in the fuel injection device.

Scheme 10: on the basis of the aspect 8, the fuel injection device is further selectively operated in the differential injection mode.

Scheme 11: on the basis of the aspect 9, the fuel injection device is further selectively operated in the differential injection mode.

Scheme 12: on the basis of any one of the aspects 1 to 5 and 7, the selection of the cylinder A is further selectively performed₁The cylinder A₂The cylinder B₁The cylinder B₂The cylinder C₁The cylinder C₂The cylinder D₁And the cylinder D₂A fuel supply is provided which supplies fuel into the cylinder during intake and/or during the first two thirds of the compression process.

Scheme 13: on the basis of the scheme 6, the cylinder A is further selectively selected₁The cylinder A₂The cylinder B₁The cylinder B₂The cylinder C₁The cylinder C₂The cylinder D₁And the cylinder D₂A fuel supply is provided which supplies fuel into the cylinder during intake and/or during the first two thirds of the compression process.

The utility model discloses aforementioned all schemes can advance oneSelectively selecting the cylinder A₁The cylinder B₁The cylinder C₁And the cylinder D₁In one direction, the cylinder A₂The cylinder B₂The cylinder C₂And the cylinder D₂In the other direction, inter-cylinder communication passages are provided between the cylinders in the same phase.

The utility model discloses in, so-called cylinder is according to four-stroke mode work or according to two-stroke mode work specifically to indicate that the cylinder sets up or sets up according to two-stroke mode work according to four-stroke mode work.

The utility model discloses in, so-called "poor time ignition mode work" means set up the ignition time difference between at least some cylinders in the cylinder that needs the ignition, and then avoids the produced huge vibration of igniteing simultaneously.

In the present invention, the term "full-point mode operation with one ignition" means an operation mode in which ignition is performed on all the other cylinders by the ignition device as long as one of the cylinders is compression-ignited in the cylinder in the compression stroke.

The utility model discloses in, so-called "one fires full point mode work when poor" indicates in the cylinder that is in compression stroke, as long as one of them cylinder is by compression ignition, just passes through ignition implements the mode of operation that has the ignition process of time difference to at least some cylinders in all the other cylinders, and its purpose is evaded the produced huge vibration of igniteing simultaneously.

The utility model discloses in, so-called "poor time injection mode work" means to set up the fuel injection time difference between at least some cylinders in the cylinder that needs injected fuel, and then avoids the produced huge vibration of simultaneous combustion and explosion.

The utility model discloses in, so-called "intercommunication passageway between jar" means the intercommunication passageway of setting between the cylinder that is in same phase place (be in same stroke simultaneously promptly), and its effect makes the cylinder that is in same phase place be in the connected state, and then eliminates or reduces the pressure differential in the cylinder that is in same phase place, and the simultaneous combustion and explosion of the cylinder that aims at realizing being in same phase place.

In the present invention, the "adjustable setting of the moment of inertia body" means that the moment of inertia of the moment of inertia body is adjusted by a dynamic means or a static means. For example, the rotational inertia of the rotary inertia body may be changed by providing an auxiliary rotary inertia body and providing a clutch adjustment device between the auxiliary rotary inertia body and the rotary inertia body.

The utility model discloses in, the inertia body be and do not last unidirectional rotation motion and only do the inertia body of swing rotation, for example the flywheel, but the one-way rotation of the inertia body alternative selection of rotation body surpasses 360.

The utility model discloses in, selectively the selection makes the inertia body (for example flywheel) includes two above sub inertia bodies, through clutch adjustment such as mechanical clutch, electromagnetic clutch the separation and reunion between the sub inertia body is switched and then is realized the purpose that the quality of the inertia body is adjustable.

The utility model discloses in, drive gear alternative selection is established to more than two to it is right to increase reciprocal active cell drive gear's transmission intensity. In this case, at least two of the transmission gears can be selectively and respectively driven by different inertia moment bodies, so as to reduce the requirement on the machining precision of related parts and improve the reliability of the related parts.

The utility model discloses in, set up the purpose of the inertia body of rotation (selectively selectable is established to the flywheel) is the kinetic energy deposit that increases the system so that the controllability and the stationarity of engine promote.

The utility model discloses in, include this number more than certain numerical value, for example include two more than two.

In the present invention, the letters "a" and "B" are added after a certain part name to distinguish two or more parts with the same name.

In the present invention, necessary components, units or systems should be installed at necessary places according to the known technology in the field of heat energy and power.

The utility model has the advantages that the engine can effectively overcome the defects of high cost, large volume, heavy weight, large vibration and the like caused by unbalanced stress of the traditional free piston engine, and has good energy-saving environmental protection performance and fuel adaptability.

Drawings

FIG. 1: the structure of embodiment 1 of the utility model is schematically shown;

FIG. 2: the structure of embodiment 2 of the utility model is schematically shown;

FIG. 3: the utility model is shown in the cross section A-A of figure 1;

FIG. 3.1: a schematic diagram of the structure of an alternative embodiment of example 3;

FIG. 3.2: a schematic structural diagram of another alternative embodiment of example 3;

in the figure: 11 cylinder A₁12 cylinders A₂13 reciprocating mover A, 14 piston A ₁15 piston A ₂21 cylinder B ₁22 cylinder B ₂23 reciprocating mover B, 24 piston B ₁25 piston B ₂31 cylinder C ₁32 cylinders C ₂33 reciprocating mover C, 34 piston C ₁35 piston C ₂41 Cylinder D ₁42 cylinder D ₂43 reciprocating mover D, 44 piston D ₁45 piston D₂And gear 51, gear AB, gear 52, gear CD, and the moment of inertia mass 6.

Detailed Description

Example 1

An engine, as shown in FIG. 1, includes a cylinder A ₁11. Cylinder A ₂12. Cylinder B ₁21. Cylinder B ₂22. Cylinder C ₁31. Cylinder C ₂32. Cylinder D ₁41. Cylinder D ₂42. A reciprocating mover A13, a reciprocating mover B23, a reciprocating mover C33, a reciprocating mover D43, a transmission gear AB51 and a transmission gear CD 52, wherein a piston A13 is arranged on the reciprocating mover A13 ₁14 and piston A ₂15, a piston B is arranged on the reciprocating mover B23 ₁24 and piston B ₂25, a piston C is arranged on the reciprocating mover C33 ₁34 and piston C ₂35, a piston D is provided on the reciprocating mover D43 ₁44 and piston D ₂45, said piston A ₁14 is arranged in the cylinder A ₁11, the piston A ₂15 is arranged in the cylinder A ₂12, the piston B ₁24 is arranged in the cylinder B ₁21, the piston B ₂25 is arranged in the cylinder B ₂22, the piston C ₁34 is arranged in the cylinder C ₁31, the piston C ₂35 is provided in the cylinder C ₂32, the piston D ₁44 is arranged in the cylinder D ₁41, the piston D ₂45 is arranged in the cylinder D ₂42, the reciprocating mover A13 is linked with the reciprocating mover B23 via the transmission gear AB51, the reciprocating mover B23 is fixedly connected with the reciprocating mover C33, the reciprocating mover C33 is linked with the reciprocating mover D43 via the transmission gear CD 52, and the cylinder A ₁11. The cylinder A ₂12. The cylinder B ₁21. The cylinder B ₂22. The cylinder C ₁31. The cylinder C ₂32. The cylinder D ₁41 and the cylinder D ₂42 operate in a four-stroke mode of operation.

Example 2

An engine, as shown in FIG. 2, includes a cylinder A ₁11. Cylinder A ₂12. Cylinder B ₁21. Cylinder B ₂22. Cylinder C ₁31. Cylinder C ₂32. Cylinder D ₁41. Cylinder D ₂42. A reciprocating mover A13, a reciprocating mover B23, a reciprocating mover C33, a reciprocating mover D43, a transmission gear AB51 and a transmission gear CD 52, wherein a piston A13 is arranged on the reciprocating mover A13 ₁14 and piston A ₂15, a piston B is arranged on the reciprocating mover B23 ₁24 and piston B ₂25, a piston C is arranged on the reciprocating mover C33 ₁34 and piston C ₂35, a piston D is provided on the reciprocating mover D43 ₁44 and piston D ₂45, said piston A ₁14 is arranged in the cylinder A ₁11, the piston A ₂15 is arranged in the cylinder A ₂12, the piston B ₁24 is arranged in the cylinder B ₁21, the piston B ₂25 is arranged in the cylinder B ₂22, the piston C ₁34 is arranged in the cylinder C ₁31, the piston C ₂35 is provided in the cylinder C ₂32, the piston D ₁44 is arranged in the cylinder D ₁41, the piston D ₂45 is arranged in the cylinder D ₂42, the reciprocating mover A13 is linked with the reciprocating mover B23 via the transmission gear AB51, the reciprocating mover B23 is fixedly connected with the reciprocating mover C33, the reciprocating mover C33 is linked with the reciprocating mover D43 via the transmission gear CD 52, and the cylinder A ₁11. The cylinder A ₂12. The cylinder B ₁21. The cylinder B ₂22. The cylinder C ₁31. The cylinder C ₂32. The cylinder D ₁41 and the cylinder D ₂42 operate in a two-stroke mode of operation.

As an alternative embodiment, the embodiments 1 and 2 and their alternative embodiments of the present invention can be further selectively selected to provide racks on both the reciprocating mover a13 and the reciprocating mover B23, and the rack on the reciprocating mover a13 is provided through the rack transmission between the transmission gear AB51 and the reciprocating mover B23, so as to realize the linkage between the reciprocating mover a13 and the reciprocating mover B23, as shown in fig. 1 and 2. Besides the transmission modes shown in the figure, other transmission modes comprising the transmission gear AB51 can be adopted to realize linkage between the reciprocating mover A13 and the reciprocating mover B23.

As an alternative embodiment, in each of the embodiments 1 and 2 and their alternative embodiments of the present invention, racks may be further selectively provided on both the reciprocating mover C33 and the reciprocating mover D43, and the racks on the reciprocating mover C33 are provided through the rack transmission on the transmission gear CD 52 and the reciprocating mover D43, thereby realizing the linkage between the reciprocating mover C33 and the reciprocating mover D43, as shown in fig. 1 and 2. Besides the transmission modes shown in the figure, other transmission modes including the transmission gear CD 52 can be adopted to realize the linkage between the reciprocating mover C33 and the reciprocating mover D43.

As an alternative embodiment, the embodiments 1 and 2 and their alternative embodiments of the present invention can be further selected such that the reciprocating mover a13 is linked to the reciprocating mover B23 through one, two (as shown), three, four, five, six, seven, eight, nine, ten, eleven, or twelve or more transmission gears AB 51. And it is further selectively possible to arrange some or all of the two or more transmission gears AB51 in the moving direction of the reciprocating mover a13 (as shown in fig. 1 to 3) or in parallel in the perpendicular direction to the moving direction of the reciprocating mover a 13.

As an alternative embodiment, the embodiments 1 and 2 and their alternative embodiments of the present invention can be further selectively selected to arrange the reciprocating mover C33 to be interlocked with the reciprocating mover D43 through one, two (as shown in the figure), three, four, five, six, seven, eight, nine, ten, eleven, or twelve or more of the transmission gears CD 52. And it is further selectively possible to arrange some or all of the two or more transmission gears CD 52 in the moving direction of the reciprocating mover D43 (as shown in fig. 1 to 3) or in parallel in the perpendicular direction to the moving direction of the reciprocating mover D43.

Example 3

An engine, as shown in fig. 3, which is different from embodiment 1 in that: the transmission gear AB51 is arranged in linkage with the rotational inertia body 6.

As an alternative embodiment, the present invention according to example 3 can also selectively make the transmission gear CD 52 and the rotational inertia body 6 to be linked (as shown in fig. 3.1) or make both the transmission gear AB51 and the transmission gear CD 52 to be linked (as shown in fig. 3.2) with the rotational inertia body 6.

As an alternative embodiment, in each of the embodiment 2 and the alternative embodiment thereof and the alternative embodiment of the embodiment 1, it is further possible to selectively provide at least one of the transmission gear AB51 and the transmission gear CD 52 in association with the inertia moment body 6.

When the engine includes more than two transmission gears AB51 and the embodiment of arranging the rotational inertia body 6 is specifically implemented, it is selectively selectable to arrange each transmission gear AB51 in linkage with one rotational inertia body 6, or to arrange a part of the transmission gears AB51 in linkage with one rotational inertia body 6, or to arrange a part or all of the transmission gears AB51 in linkage with the same rotational inertia body 6.

When the engine includes more than two transmission gears CD 52 and the embodiment of arranging the rotational inertia body 6 is implemented, it is selectively possible to arrange each transmission gear CD 52 in linkage with one rotational inertia body 6, or arrange a part of the transmission gears CD 52 in linkage with one rotational inertia body 6, or arrange a part or all of the transmission gears CD 52 in linkage with the same rotational inertia body 6.

When the engine comprises more than two transmission gears AB51, more than two transmission gears CD 52 and the rotational inertia body 6, it is possible to selectively and selectively arrange some or all of the transmission gears AB51 and some or all of the transmission gears CD 52 in linkage with the same rotational inertia body 6.

When the engine comprises one transmission gear AB51 and one transmission gear CD 52, the transmission gear AB51 and the transmission gear CD 52 can further selectively share one rotational inertia body 6.

In the specific implementation of all the aforementioned embodiments of the present invention including the rotational inertia body 6, the transmission gear AB51 and/or the transmission gear CD 52 may be selectively connected to the rotational inertia body 6 directly (as shown in fig. 3), or the transmission gear AB51 and/or the transmission gear CD 52 may be linked to the rotational inertia body 6 via a transmission unit or a transmission element.

In the present invention, all the embodiments including the inertia moment body 6 as the changeable embodiments can be further selectively set to adjust the inertia moment of the inertia moment body 6.

As an alternative embodiment, all the above embodiments of the present invention including the rotational inertia bodies 6 may further selectively select at least one of the rotational inertia bodies 6 to be a motor rotor or a part of a motor rotor; and the motor can be further selectively set as a generator, a motor or a generator motor.

The utility model discloses aforementioned all embodiments when concrete implementation cylinder A ₁11. The cylinder A ₂12. The cylinder B ₁21. The cylinder B ₂22. The cylinder C ₁31. The cylinder C ₂32. The cylinder D ₁41 and the cylinder D₂An ignition device is arranged in the cylinder 42; and further selectively enabling said ignition device to operate in a differential ignition mode; or, the ignition device is enabled to work according to a full ignition mode; or, operating the ignition device in a full-point mode at a single-differential-time.

In the specific implementation of all the aforementioned embodiments of the present invention, the cylinder a can be selectively selected₁11. The cylinder A ₂12. The cylinder B ₁21. The cylinder B ₂22. The cylinder C ₁31. The cylinder C ₂32. The cylinder D ₁41 and the cylinder D₂42 a fuel injection device is arranged; and further selectively selecting operation of said fuel injection means in a differential injection mode.

As a changeable embodiment, all the previous embodiments of the present invention can be selectively selected to be on the cylinder A when the present invention is implemented₁11. The cylinder A ₂12. The cylinder B ₁21. The cylinder B ₂22. The cylinder C ₁31. The cylinder C ₂32. The cylinder D ₁41 and the cylinder D₂A fuel supply is provided in 42 which supplies fuel into the cylinder during intake and/or during the first two thirds of the compression process.

In the concrete implementation of all the aforementioned embodiments of the present invention, it is preferable to make the cylinder a₁11. The cylinder B ₁21. The cylinder C ₁31 and the cylinder D ₁41 in one direction, said cylinder a₂12. The cylinder B ₂22. The cylinder C ₂32 and the cylinder D ₂42 in the other direction, and inter-cylinder communication passages are provided between the cylinders in the same phase; and the cylinders in the same phase can be further selectively communicated in series or in parallel through the inter-cylinder communication passage.

The utility model discloses set up intercommunication passageway's effect between the jar makes the cylinder that is in same phase place be in the connected state, and then eliminates or reduces the pressure differential in the cylinder that is in same phase place, and the simultaneous combustion and explosion of cylinder that aims at realizing being in same phase place.

In the specific implementation of all the aforementioned embodiments of the present invention, the diameters of the pistons of the reciprocating mover a13, the reciprocating mover B23, the reciprocating mover C33 and the reciprocating mover D43 may be set to be the same selectively.

The utility model discloses it is aforementioned that the embodiment when concrete implementation, but at least some cylinders in the cylinder of the same phase place that selective selection made needs the ignition set up the ignition time difference to avoid the produced huge vibration of igniteing simultaneously.

The utility model discloses aforementioned all embodiments still can selectively select to make the cylinder that is in the compression stroke simultaneously when concrete implementation, as long as one of them cylinder is by compression ignition, just pass through ignition carries out the mode of operation that has the ignition process of time difference to all the other all at least some cylinders in the cylinder of compression stroke, and its purpose is to avoid the produced huge vibration of simultaneous ignition.

The utility model discloses when concrete implementation, but also the selectivity makes the cylinder that is in the compression stroke simultaneously, as long as one of them cylinder is by compression ignition, just through ignition carries out the mode of igniteing to all the other cylinders that are in the compression stroke.

The utility model discloses aforementioned all embodiments still can selectively make and set up the fuel injection time difference between at least some cylinders in the cylinder that needs injected fuel when concrete implementation, and then avoid the produced huge vibration of simultaneous combustion and explosion.

In the present invention, when implementing all the aforementioned embodiments including the rotational inertia body 6, the setting of the rotational inertia body 6 can be further selectively selected, and the setting of the rotational inertia body 6 can be specifically changed by setting an auxiliary rotational inertia body and providing a clutch adjustable device between the auxiliary rotational inertia body and the rotational inertia body 6; the rotary inertia body 6 (such as a flywheel) can also selectively comprise more than two sub rotary inertia bodies, and the purpose of adjusting the mass of the rotary inertia body is achieved by adjusting the clutch switching between the sub rotary inertia bodies through a mechanical clutch, an electromagnetic clutch and other clutches.

The utility model discloses aforementioned all contain the implementation of the inertia body 6 is when concrete implementation, the inertia body 6 is not done and is lasted unidirectional rotation motion and only do the swing and rotate, and alternative selection makes the swing angle of the inertia body 6 exceeds 360, the selective selection of the inertia body 6 is established to the flywheel.

In an alternative embodiment, all the previous embodiments of the present invention may be implemented by selectively making some of the cylinders in the same phase (i.e. in the same stroke), preferably making the cylinder a in the same phase (i.e. in the same stroke at the same time)₁11. The cylinder B ₂22. The cylinder C ₂32 and a cylinder D ₁41 are in the same phase, so that the cylinder A ₂12. The cylinder B ₁21. The cylinder C ₁31 and the cylinder D ₂42 are in the same phase.

The single-direction arrows in the figures represent the intake or exhaust direction; the double-headed arrow represents a movement direction of the reciprocating mover, and a solid-line arrow direction of the double-headed arrow is a movement direction of the reciprocating mover at a certain moment of the engine, and a dotted-line arrow direction of the double-headed arrow is a movement direction of the reciprocating mover at another certain moment of the engine.

The utility model discloses aforementioned all embodiments the distribution valve of engine realizes through automatically controlled or cam control.

The utility model discloses in, the drawing only is a signal, and any technical scheme that satisfies this application writing and record all belongs to the scope of protection of this application.

Obviously, the present invention is not limited to the above embodiments, and many modifications can be derived or suggested according to the known technology in the field and the technical solutions disclosed in the present invention, and all of these modifications should also be considered as the protection scope of the present invention.

Claims

1. An engine comprises a cylinder A₁(11) Cylinder A₂(12) Cylinder B₁(21) Cylinder B₂(22) And a cylinder C₁(31) And a cylinder C₂(32) Cylinder D₁(41) Cylinder D₂(42) Reciprocating rotor A (13), reciprocating rotor B (23), reciprocating rotor C (33), reciprocating rotor D (43), transmission gear AB (51) and transmission gear CD (52), its characterized in that: a piston A is arranged on the reciprocating mover A (13)₁(14) And piston A₂(15) A piston B (23) is arranged on the reciprocating mover B₁(24) And piston B₂(25) A piston C is arranged on the reciprocating mover C (33)₁(34) And piston C₂(35) A piston D is arranged on the reciprocating mover D (43)₁(44) And a piston D₂(45) Said piston A₁(14) Is arranged at the cylinder A₁(11) Inner, the piston A₂(15) Is arranged at the cylinder A₂(12) Inner, the piston B₁(24) Is arranged in the cylinder B₁(21) Inner, the piston B₂(25) Is arranged in the cylinder B₂(22) Inner, the piston C₁(34) Is arranged in the cylinder C₁(31) Inner, the piston C₂(35) Is arranged in the cylinder C₂(32) Inner, the piston D₁(44) Is arranged in the cylinder D₁(41) Inner, the piston D₂(45) Is arranged in the cylinder D₂(42) The reciprocating rotor A (13) is in linkage with the reciprocating rotor B (23) through the transmission gear AB (51), the reciprocating rotor B (23) is fixedly connected with the reciprocating rotor C (33), the reciprocating rotor C (33) is in linkage with the reciprocating rotor D (43) through the transmission gear CD (52), and the cylinder A₁(11) The cylinder A₂(12) The cylinder B₁(21) The cylinder B₂(22) The cylinder C₁(31) The cylinder C₂(32) The cylinder D₁(41) And the cylinder D₂(42) Operating in a four-stroke mode of operation or in a two-stroke mode of operation.

2. The engine of claim 1, wherein: at least one of the transmission gear AB (51) and the transmission gear CD (52) is arranged in linkage with the rotational inertia body (6).

3. The engine of claim 2, wherein: the rotational inertia of the rotational inertia body (6) is adjustable.

4. The engine of claim 2, wherein: the inertia moment body (6) is provided as or as part of the motor rotor.

5. An engine as set forth in claim 3 wherein: the inertia moment body (6) is provided as or as part of the motor rotor.

6. The engine of any one of claims 1-5, characterized in that: the cylinder A₁(11) The cylinder A₂(12) The cylinder B₁(21) The cylinder B₂(22) The cylinder C₁(31) Said gasCylinder C₂(32) The cylinder D₁(41) And the cylinder D₂(42) An ignition device is arranged in the device.

7. The engine of claim 6, wherein: the ignition device works in an differential ignition mode; or, the ignition device works according to a full ignition mode; or, the ignition device operates in a full-point mode at a single firing difference.

8. The engine of any one of claims 1-5 and 7, characterized in that: the cylinder A₁(11) The cylinder A₂(12) The cylinder B₁(21) The cylinder B₂(22) The cylinder C₁(31) The cylinder C₂(32) The cylinder D₁(41) And the cylinder D₂(42) A fuel injection device is arranged in the fuel injection device.

9. The engine of claim 6, wherein: the cylinder A₁(11) The cylinder A₂(12) The cylinder B₁(21) The cylinder B₂(22) The cylinder C₁(31) The cylinder C₂(32) The cylinder D₁(41) And the cylinder D₂(42) A fuel injection device is arranged in the fuel injection device.

10. The engine of claim 8, wherein: the fuel injection device operates in a differential injection mode.

11. The engine of claim 9, wherein: the fuel injection device operates in a differential injection mode.

12. The engine of any one of claims 1-5 and 7, characterized in that: the cylinder A₁(11) The cylinder A₂(12) The cylinder B₁(21) The cylinder B₂(22) The cylinder C₁(31) The cylinder C₂(32) The cylinder D₁(41) And the cylinder D₂(42) A fuel supply is provided which supplies fuel into the cylinder during intake and/or during the first two thirds of the compression process.

13. The engine of claim 6, wherein: the cylinder A₁(11) The cylinder A₂(12) The cylinder B₁(21) The cylinder B₂(22) The cylinder C₁(31) The cylinder C₂(32) The cylinder D₁(41) And the cylinder D₂(42) A fuel supply is provided which supplies fuel into the cylinder during intake and/or during the first two thirds of the compression process.

14. The engine of any one of claims 1 to 5 and 7 and 9 to 11 and 13, wherein: the cylinder A₁(11) The cylinder B₁(21) The cylinder C₁(31) And the cylinder D₁(41) In one direction, the cylinder A₂(12) The cylinder B₂(22) The cylinder C₂(32) And the cylinder D₂(42) In the other direction, inter-cylinder communication passages are provided between the cylinders in the same phase.

15. The engine of claim 6, wherein: the cylinder A₁(11) The cylinder B₁(21) The cylinder C₁(31) And the cylinder D₁(41) In one direction, the cylinder A₂(12) The cylinder B₂(22) The cylinder C₂(32) And the cylinder D₂(42) In the other direction, inter-cylinder communication passages are provided between the cylinders in the same phase.

16. The engine of claim 8, wherein: the cylinder A₁(11) The cylinder B₁(21) The cylinder C₁(31) And the cylinder D₁(41) In one directionTo the cylinder A₂(12) The cylinder B₂(22) The cylinder C₂(32) And the cylinder D₂(42) In the other direction, inter-cylinder communication passages are provided between the cylinders in the same phase.

17. The engine of claim 12, wherein: the cylinder A₁(11) The cylinder B₁(21) The cylinder C₁(31) And the cylinder D₁(41) In one direction, the cylinder A₂(12) The cylinder B₂(22) The cylinder C₂(32) And the cylinder D₂(42) In the other direction, inter-cylinder communication passages are provided between the cylinders in the same phase.