CN111663999A - Engine - Google Patents
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- CN111663999A CN111663999A CN202010465928.2A CN202010465928A CN111663999A CN 111663999 A CN111663999 A CN 111663999A CN 202010465928 A CN202010465928 A CN 202010465928A CN 111663999 A CN111663999 A CN 111663999A
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- cylinder
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- reciprocating
- engine
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- 239000000446 fuel Substances 0.000 claims abstract description 26
- 230000005540 biological transmission Effects 0.000 claims description 60
- 238000002347 injection Methods 0.000 claims description 20
- 239000007924 injection Substances 0.000 claims description 20
- 238000010304 firing Methods 0.000 claims description 2
- 230000007547 defect Effects 0.000 abstract description 4
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 238000007906 compression Methods 0.000 description 11
- 230000006835 compression Effects 0.000 description 8
- 230000033001 locomotion Effects 0.000 description 8
- 238000004891 communication Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 5
- 238000002485 combustion reaction Methods 0.000 description 4
- 238000004880 explosion Methods 0.000 description 4
- 239000000243 solution Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004146 energy storage Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B71/00—Free-piston engines; Engines without rotary main shaft
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B71/00—Free-piston engines; Engines without rotary main shaft
- F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
Abstract
The invention discloses an engine, wherein a piston A is arranged on a reciprocating rotor A1And piston A2A piston BC is arranged on the reciprocating mover BC1And piston BC2A 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 and outer pistons BC1Arranged in a cylinder BC1Inner and outer pistons BC2Arranged in a cylinder BC2Inner, piston D1Arranged in a cylinder D1Inner, piston D2Arranged in a cylinder D2And the ratio of the diameter of a piston on the reciprocating rotor BC to the diameter of a piston on the reciprocating rotor A or the ratio of the diameter of a piston on the reciprocating rotor BC to the diameter of a piston on the reciprocating rotor D is between 1.35 and 1.5. The invention discloses an engineThe defects of high manufacturing cost, large volume, heavy weight, large vibration and the like caused by unbalanced stress of the traditional free piston engine are effectively overcome, and the engine has good energy-saving and environment-friendly properties and fuel adaptability.
Description
Technical Field
The invention relates to the field of heat energy and power, in particular 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.
Disclosure of Invention
In order to solve the above problems, the technical solution proposed by the present invention is as follows:
scheme 1: an engine comprises a cylinder A1Cylinder A2Cylinder BC1Cylinder BC2Cylinder D1Cylinder D2The reciprocating rotor A is provided with a piston A, a reciprocating rotor BC, a reciprocating rotor D, a transmission gear AB and a transmission gear CD1And piston A2A piston BC is arranged on the reciprocating mover BC1And piston BC2A 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 BC1Is arranged on the cylinder BC1Inner, the piston BC2Is arranged on the cylinder BC2Inner, 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 BC through the transmission gear AB, the reciprocating rotor BC is in linkage with the reciprocating rotor D through the transmission gear CD, and the ratio of the diameter of a piston on the reciprocating rotor BC to the diameter of the piston on the reciprocating rotor A or the activity on the reciprocating rotor BCThe ratio of the diameter of the plug to the diameter of the piston on the reciprocating mover D is between 1.35 and 1.5, and the cylinder A1The cylinder A2The cylinder BC1The cylinder BC2The 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 rotary inertia of the rotary inertia body is further selectively and adjustably set.
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 operated1The cylinder A2The cylinder BC1The cylinder BC2The 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 works according to a full ignition mode; or, the ignition device operates in a full-point mode at a single firing difference.
Scheme 8: further selectively operating the cylinder a on the basis of any one of the aspects 1 to 5 and 71The cylinder A2The cylinder BC1The cylinder BC2The 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 enabled1The cylinder A2The cylinder BC1The cylinder BC2The 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 BC1The cylinder BC2The 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 air cylinder A is further selectively arranged1The cylinder A2The cylinder BC1The cylinder BC2The 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.
All the schemes of the invention can be further selectively selected to enable the cylinder A1The cylinder BC1And the cylinder D1In one direction, the cylinder A2The cylinder BC2And the cylinder D2In the other direction, inter-cylinder communication passages are provided between the cylinders in the same phase.
In the present invention, the ratio of the diameter of the piston of the reciprocating mover BC to the diameter of the piston of the reciprocating mover a or the ratio of the diameter of the piston of the reciprocating mover BC to the diameter of the piston of the reciprocating mover D may be selectively selected to be 1.41.
In the present invention, the "differential ignition mode operation" means that an ignition time difference is provided between at least some of the cylinders requiring ignition, and large vibration caused by simultaneous ignition is avoided.
In the present invention, the "operation in the one-ignition full-ignition mode" refers to an operation mode in which, in the cylinders in the compression stroke, ignition is performed on all the remaining cylinders by the ignition device as long as one of the cylinders is compression-ignited.
In the present invention, the "operation in the full-point mode with one-time difference" means an operation mode in which, in the cylinders in the compression stroke, an ignition process with a time difference is performed on at least some of the remaining total cylinders by the ignition device as long as one of the cylinders is compression-ignited, with the object of avoiding large vibrations caused by simultaneous ignition.
In the present invention, the "differential injection mode operation" means that a fuel injection time difference is provided between at least some of the cylinders in which fuel is to be injected, thereby avoiding a large vibration caused by simultaneous combustion and explosion.
In the present invention, the "inter-cylinder communication passage" refers to a communication passage provided between cylinders in the same phase (i.e., in the same stroke at the same time), and is used to communicate the cylinders in the same phase, thereby eliminating or reducing the pressure difference in the cylinders in the same phase, and achieving simultaneous combustion and explosion of the cylinders in the same phase.
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.
In the present invention, the rotational inertia body refers to an inertia body which does not perform continuous unidirectional rotation motion but performs only swinging rotation, such as a flywheel, and unidirectional rotation of the rotational inertia body can be selectively selected to exceed 360 °.
In the invention, the rotary inertia body (such as a flywheel) can be selectively selected to comprise more than two sub rotary inertia bodies, and the purpose of adjusting the mass of the rotary inertia body is realized by adjusting the clutch switching between the sub rotary inertia bodies through clutches such as a mechanical clutch, an electromagnetic clutch and the like.
In the invention, the number of the transmission gears can be selectively set to be more than two so as to increase the transmission strength of the reciprocating rotor to the transmission gears. In this case, at least two of the transmission gears can be selectively and respectively driven by different inertia moment bodies, so that the requirement on the machining precision of related parts is reduced, and the reliability is improved.
In the invention, the rotational inertia body (optionally set as a flywheel) is arranged to increase the kinetic energy reserve of the system so as to improve the controllability and the stability of the engine.
In the invention, the fact that the cylinder works according to the four-stroke working mode or works according to the two-stroke working mode specifically means that the cylinder works and is arranged according to the four-stroke working mode or works and is arranged according to the two-stroke working mode.
In the present invention, the addition of letters such as "a" and "B" to a name of a certain component is merely to distinguish two or more components having the same name.
In the present invention, necessary components, units, systems, etc. should be provided where necessary according to the well-known techniques in the thermal and power fields.
The engine disclosed by the invention has the beneficial effects that the defects of high manufacturing cost, large volume, heavy weight, large vibration and the like caused by unbalanced stress of the traditional free piston engine can be effectively overcome, and the engine has good energy-saving and environment-friendly properties and fuel adaptability.
Drawings
FIG. 1: the structure of embodiment 1 of the invention is schematically shown;
FIG. 2: the structure of embodiment 2 of the invention is schematically shown;
FIG. 3: FIG. 1 is a sectional view A-A of the present invention;
FIG. 3.1: a schematic structural diagram of a variation implementation of embodiment 3 of the present invention;
FIG. 3.2: a schematic structural diagram of another alternative embodiment of example 3 of the present invention;
in the figure: 11 cylinder A112 cylinders A213 reciprocating mover A, 14 piston A 115 piston A 221 cylinder BC 122 cylinder BC 223 reciprocating mover BC, 24 piston BC 125 piston BC 231 cylinder D 132 cylinders D 233 reciprocating mover D, 34 piston D 135 piston D2Gear 41, gear AB, gear 42, gear CD, 5 moment of inertia.
Detailed Description
Example 1
An engine, as shown in FIG. 1, includes a cylinder A 111. Cylinder A 212. Cylinder BC121. Cylinder BC222. Cylinder D 131. Cylinder D 232. A reciprocating mover A13, a reciprocating mover BC 23, a reciprocating mover D33, a transmission gear AB 41 and a transmission gear CD42, wherein a piston A13 is arranged on the reciprocating mover A13 114 and piston A 215, a piston BC 23 is provided on the reciprocating mover BC 124 and piston BC 225, a piston D is provided on the reciprocating mover D33 134 and piston D 235, the piston A 114 is arranged in the cylinder A 111, the piston A 215 is arranged in the cylinder A 212, the piston BC 124 is arranged in the cylinder BC 121, the piston BC 225 is provided in the cylinder BC 222, the piston D 134 is arranged in the cylinder D 131, the piston D 235 is provided in the cylinder D2In the chamber 32, the reciprocating mover a13 is linked with the reciprocating mover BC 23 via two transmission gears AB 41, the reciprocating mover BC 23 is linked with the reciprocating mover D33 via two transmission gears CD42, a ratio of a diameter of a piston on the reciprocating mover BC 23 to a diameter of a piston on the reciprocating mover a13 is 1.41, a diameter of a piston on the reciprocating mover a13 is the same as the diameter of the piston on the reciprocating mover D33, and the cylinder a is provided111. The cylinderA 212. The cylinder BC 121. The cylinder BC 222. The cylinder D 131 and the cylinder D 232 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 BC121. Cylinder BC222. Cylinder D 131. Cylinder D 232. A reciprocating mover A13, a reciprocating mover BC 23, a reciprocating mover D33, a transmission gear AB 41 and a transmission gear CD42, wherein a piston A13 is arranged on the reciprocating mover A13 114 and piston A 215, a piston BC 23 is provided on the reciprocating mover BC124 and piston BC225, a piston D is provided on the reciprocating mover D33 134 and piston D 235, the piston A 114 is arranged in the cylinder A 111, the piston A 215 is arranged in the cylinder A 212, the piston BC124 is arranged in the cylinder BC121, the piston BC225 is provided in the cylinder BC222, the piston D 134 is arranged in the cylinder D 131, the piston D 235 is provided in the cylinder D2In 32, the reciprocating mover a13 is linked with the reciprocating mover BC 23 through two transmission gears AB 41, the reciprocating mover BC 23 is linked with the reciprocating mover D33 through two transmission gears CD42, a ratio of a diameter of a piston on the reciprocating mover BC 23 to a diameter of a piston on the reciprocating mover a13 is 1.35, the diameter of the piston on the reciprocating mover a13 is the same as the diameter of the piston on the reciprocating mover D33, and the cylinder a is provided111. The cylinder A 212. The cylinder BC 121. The cylinder BC 222. The cylinder D 131 and the cylinder D 232 operate in a two-stroke mode of operation.
As alternative embodiments, in addition to the ratio between the piston diameters defined in examples 1 and 2, examples 1 and 2 of the present invention may also be selected such that the ratio between the piston diameter on the reciprocating mover BC 23 and the piston diameter on the reciprocating mover a13 is between 1.35 and 1.5, or the ratio between the piston diameter on the reciprocating mover BC 23 and the piston diameter on the reciprocating mover D33 is between 1.35 and 1.5. And may be specifically and selectively selected such that the ratio of the piston diameter on the reciprocating mover BC 23 to the piston diameter on the reciprocating mover a13 is 1.36, 1.37, 1.38, 1.39, 1.4, 1.41, 1.42, 1.43, 1.44, 1.45, 1.46, 1.47, 1.48, 1.49, or 1.5; the ratio of the piston diameter on the reciprocating mover BC 23 to the piston diameter on the reciprocating mover D33 may also be selected to be 1.36, 1.37, 1.38, 1.39, 1.4, 1.41, 1.42, 1.43, 1.44, 1.45, 1.46, 1.47, 1.48, 1.49 or 1.5; it is further preferable that a diameter of a piston of the reciprocating mover a13 is set to be the same as a diameter of a piston of the reciprocating mover D33.
As an alternative embodiment, in each of the embodiments 1 and 2 of the present invention and their alternative embodiments, racks may be further selectively provided on both the reciprocating mover a13 and the reciprocating mover BC 23, and the racks on the reciprocating mover a13 are provided to be driven by the racks on the reciprocating mover BC 23 through the transmission gear AB 41, thereby realizing the linkage between the reciprocating mover a13 and the reciprocating mover BC 23, as specifically shown in fig. 1 and 2. Besides the transmission modes shown in the figure, other transmission modes comprising the transmission gear AB 41 can be adopted to realize linkage between the reciprocating mover A13 and the reciprocating mover BC 23.
As an alternative embodiment, the embodiments 1 and 2 and their alternative embodiments of the present invention may be further provided with another rack on the reciprocating mover BC 23, and the racks on the reciprocating mover D33, respectively, and the racks on the reciprocating mover BC 23 are provided with the rack transmission on the reciprocating mover D33 via the transmission gear CD42, thereby realizing the linkage between the reciprocating mover BC 23 and the reciprocating mover D33, as shown in fig. 1 and 2. Besides the transmission modes shown in the figures, other transmission modes including the transmission gear CD42 can be adopted to realize the linkage between the reciprocating mover BC 23 and the reciprocating mover D33.
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 a13 to be interlocked with the reciprocating mover BC 23 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 AB 41. And it is further possible to selectively arrange two or more of the transmission gears AB 41 in the moving direction of the reciprocating mover a13 (as shown in fig. 1 to 3) or in parallel in the direction perpendicular 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 BC 23 in linkage with the reciprocating mover D33 via 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 42. And it is further possible to selectively arrange two or more of the transmission gears CD42 in the moving direction of the reciprocating mover D33 (as shown in fig. 1 to 3) or in parallel in the perpendicular direction to the moving direction of the reciprocating mover D33.
Example 3
An engine, as shown in fig. 3, which is different from embodiment 1 in that: the transmission gear AB 41 is arranged in linkage with the rotational inertia body 5, and the transmission gear CD42 is arranged in linkage with the other rotational inertia body 5.
As alternative embodiments, the present invention in example 3 may also selectively couple the transmission gear CD42 with the inertia mass 5 (as shown in fig. 3.1) or couple the transmission gear AB 41 with the inertia mass 5 (as shown in fig. 3.2).
As an alternative embodiment, the present invention can be further selectively applied to at least one of the transmission gear AB 41 and the transmission gear CD42 in association with the inertia moment body 5, in each of the embodiment 2 and the alternative embodiment thereof and the alternative embodiment of the embodiment 1.
In the specific implementation of all the aforementioned embodiments including the rotational inertia body 5, the transmission gear AB 41 and/or the transmission gear CD42 may be selectively and directly connected to the rotational inertia body 5 (as shown in fig. 3), or the transmission gear AB 41 and/or the transmission gear CD42 may be selectively and jointly disposed with the rotational inertia body 5 through a transmission unit or a transmission element.
When the engine includes more than two transmission gears AB 41 and the rotational inertia body 5 is implemented, it is selectively possible to couple each of the transmission gears AB 41 to one rotational inertia body 5, or couple a part or all of the transmission gears AB 41 to the same rotational inertia body 5.
When the engine includes more than two transmission gears CD42 and the rotational inertia body 5 is implemented, it is selectively possible to couple each transmission gear CD42 with one rotational inertia body 5, or couple a part of the transmission gears CD42 with one rotational inertia body 5, or couple a part or all of the transmission gears CD42 with the same rotational inertia body 5.
When the engine comprises more than two transmission gears AB 41 and more than two transmission gears CD42 and the embodiment of the rotational inertia mass 5 is implemented, part or all of the transmission gears AB 41 and part or all of the transmission gears CD42 can be selectively linked with the same rotational inertia mass 5.
As an alternative embodiment, all the aforementioned embodiments of the present invention including the inertia moment body 5 may be further implemented to selectively make the inertia moment body 5 have an adjustable inertia moment.
As an alternative embodiment, all the aforementioned embodiments of the present invention that include the rotational inertia bodies 5 may further selectively make at least one of the rotational inertia bodies 5 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.
As alternative embodiments, all the aforementioned embodiments of the present invention may be further selectively selected in the cylinder A in practical applications 111. The cylinder A 212. The cylinder BC 121. The cylinder BC 222. The cylinder D 131 and the cylinder D2An ignition device is arranged in the chamber 32; and can further choose to make the said ignition device work according to the ignition mode of difference selectively; 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 above embodiments of the invention, the cylinder A can be selectively selected111. The cylinder A 212. The cylinder BC 121. The cylinder BC 222. The cylinder D 131 and the cylinder D 232, a fuel injection device is arranged in the fuel tank; 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 invention can be selectively selected in the cylinder A 111. The cylinder A 212. The cylinder BC 121. The cylinder BC 222. The cylinder D 131 and the cylinder D2A fuel supply is provided within 32 and is further selectively operable to supply fuel into the cylinder during intake and/or during the first two thirds of the compression process.
In the specific implementation of all the aforementioned embodiments of the present invention, it is preferable that the cylinder A is made of a material having a high hardness 111. The cylinder BC121 and the cylinder D 131 in one direction, said cylinder a212. The cylinder BC222 and the cylinder D 232 in the other direction, in the same phaseAn inter-cylinder communication channel is arranged between the cylinders; and the cylinders in the same phase can be further selectively communicated in series or in parallel through the inter-cylinder communication passage.
In particular implementation, at least a part of the cylinders with the same phase needing ignition can be selectively selected to be provided with ignition time differences so as to avoid huge vibration generated by simultaneous ignition.
When the aforesaid all the embodiments of the present invention are implemented specifically, the cylinders which are simultaneously in the compression stroke can be selectively selected, and as long as one of the cylinders is compression-ignited, the operation mode of the ignition process with the time difference is implemented on at least part of the rest of the cylinders which are all in the compression stroke through the ignition device, so as to avoid the huge vibration generated by the simultaneous ignition.
When the above embodiments of the invention are implemented, the operation mode that the cylinders which are simultaneously in the compression stroke are selected, and the rest of the cylinders which are all in the compression stroke are ignited by the ignition device as long as one of the cylinders is subjected to compression ignition can be selected selectively.
In the specific implementation of all the embodiments of the invention, the fuel injection time difference can be selectively set among at least one part of the cylinders needing to inject the fuel, so that the huge vibration generated by simultaneous combustion and explosion is avoided.
The function of the inter-cylinder communication channel is to enable the cylinders in the same phase to be in a communication state, so that the pressure difference in the cylinders in the same phase is eliminated or reduced, and the purpose of simultaneous combustion and explosion of the cylinders in the same phase is realized.
In the specific implementation of all the aforementioned embodiments including the rotational inertia body 5, the setting of the rotational inertia body 5 may be further selectively selected, and specifically, the setting of the rotational inertia body 5 may be changed by providing an auxiliary rotational inertia body and providing a clutch adjustable device between the auxiliary rotational inertia body and the rotational inertia body 5; the rotary inertia body 5 (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.
In the specific implementation of all the aforementioned embodiments including the inertia moment body 5, the inertia moment body 5 does not perform a continuous unidirectional rotation motion but performs only a swinging motion, the swinging angle of the inertia moment body 5 may be selectively made to exceed 360 °, and the inertia moment body 5 may be selectively set as a flywheel.
As an alternative embodiment, all the previous embodiments of the present invention can be implemented by selectively making some cylinders in the same phase (i.e. in the same stroke), preferably making the cylinder A in the same phase 111. The cylinder BC222 and a cylinder D 131 in the same phase, making the cylinder A 212. The cylinder BC121 and the cylinder D 232 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.
In the invention, the valve of the engine is realized by electric control or cam control.
In the present invention, the attached drawings are only schematic, and any technical solutions meeting the written description of the present application belong to the protection scope of the present 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 the modifications should be considered as the protection scope of the present invention.
Claims (10)
1. An engine comprises a cylinder A1(11) Cylinder A2(12) Cylinder BC1(21) Cylinder BC2(22) Cylinder D1(31) Cylinder D2(32) Reciprocating rotor A (13), reciprocating rotor BC (23), reciprocating rotor D (33), transmission gear AB (41) and transmission gear CD (42), its characterized in that: a piston A is arranged on the reciprocating mover A (13)1(14) And piston A2(15) A piston BC (23) is provided on the reciprocating mover BC1(24) And piston BC2(25) A piston D is arranged on the reciprocating mover D (33)1(34) And a piston D2(35) 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 BC1(24) Is arranged on the cylinder BC1(21) Inner, the piston BC2(25) Is arranged on the cylinder BC2(22) Inner, the piston D1(34) Is arranged in the cylinder D1(31) Inner, the piston D2(35) Is arranged in the cylinder D2(32) The reciprocating rotor A (13) is in linkage with the reciprocating rotor BC (23) through the transmission gear AB (41), the reciprocating rotor BC (23) is in linkage with the reciprocating rotor D (33) through the transmission gear CD (42), the ratio of the diameter of a piston on the reciprocating rotor BC (23) to the diameter of the piston on the reciprocating rotor A (13) or the ratio of the diameter of the piston on the reciprocating rotor BC (23) to the diameter of the piston on the reciprocating rotor D (33) is between 1.35 and 1.5, and the cylinder A1(11) The cylinder A2(12) The cylinder BC1(21) The cylinder BC2(22) The cylinder D1(31) And the cylinder D2(32) 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 (41) and the transmission gear CD (42) is arranged in linkage with the rotational inertia body (5).
3. The engine of claim 2, wherein: the rotational inertia of the rotational inertia body (5) is adjustable.
4. The engine of claim 2, wherein: the inertia moment body (5) is provided as a motor rotor or as a part of a motor rotor.
5. An engine as set forth in claim 3 wherein: the inertia moment body (5) is provided as a motor rotor or as a part of a 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 BC1(21) The cylinder BC2(22) The cylinder D1(31) And the cylinder D2(32) 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 BC1(21) The cylinder BC2(22) The cylinder D1(31) And the cylinder D2(32) 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 BC1(21) The cylinder BC2(22) The cylinder D1(31) And the cylinder D2(32) A fuel injection device is arranged in the fuel injection device.
10. An engine as set forth in claim 8 or 9 wherein: the fuel injection device operates in a differential injection mode.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2020103090109 | 2020-04-19 | ||
| CN202010309010 | 2020-04-19 |
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| CN111663999A true CN111663999A (en) | 2020-09-15 |
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| CN202020939414.1U Expired - Fee Related CN213298112U (en) | 2020-04-19 | 2020-05-28 | Engine |
| CN202010465928.2A Pending CN111663999A (en) | 2020-04-19 | 2020-05-28 | Engine |
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| CN213298112U (en) * | 2020-04-19 | 2021-05-28 | 熵零技术逻辑工程院集团股份有限公司 | Engine |
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