CN1033600C - Reciprocatory machines - Google Patents
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- CN1033600C CN1033600C CN 86106958 CN86106958A CN1033600C CN 1033600 C CN1033600 C CN 1033600C CN 86106958 CN86106958 CN 86106958 CN 86106958 A CN86106958 A CN 86106958A CN 1033600 C CN1033600 C CN 1033600C
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Abstract
The present invention relates to a reciprocating engine which is provided with a cylinder (12). At least one piston (18) limits a working chamber (13a). The piston does reciprocating movement in the cylinder by a crankshaft (40). A steam inlet (26) and a steam exhaust port (27) of the reciprocating engine are arranged at the opposite ends of a working part of the cylinder, and are respectively provided with a steam valve (10) and a steam valve (11) and a piston for opening and closing the steam inlet and the steam exhaust port. The steam valves are driven by the crankshaft (40), and are provided with a mechanism (68) which can regulate the timing relationship among the displacements of the crankshaft and the steam valves and further regulate the timing relationship between the steam valves. The timing regulation in the steam opening positions on the opposite ends of the working part of the cylinder is greater than the adjustment regulation in the arrangement of steam openings which are conventionally and mutually separated.
Description
The present invention broadly says so and belongs to reciprocating machine, but says with regard to its concrete property aspect, and it is one and has two-stroke, is furnished with the internal-combustion engine of spark ignition or compressible igniting.
As everyone knows, experience for a long time shows that internal-combustion engine will realize that the running of coordinating is very difficult.People know that also to the motor of conventional engine and other type, change air inlet and exhaust valve valve timing is normally realized by means of the angle relation between adjusting bent axle and the air valve distribution cam axle.Be to regulate the valve timing between bent axle and the air valve distribution cam axle, people have proposed some inherent measures, and for example british patent specification 2,109, disclose air inlet and exhaust valve in No. 858 and are furnished with separately camshaft respectively, carry out adjusting separately.It is said that this adjusting can realize the variation of any needs at the valve overlap angle of air inlet and exhaust valve.
On the other hand, when gas port was made valve by opposed pistons separately, people also took measures to regulate the phase relationship between the opposed pistons, D.B.P. 616, No. 451, U. S. Patent 2,113,480 and 2, in 401, No. 188 and the B. P. 584,783 this measure has been proposed.Under latter event, suction port is equipped with a pressurized machine.In these motors, the adjusting of piston timing for example corresponding to engine load, has obvious effects to changing compression ratio, and this has changed the air valve valve timing with regard to meaning inherently.Yet it obviously can not carry out independent regulation to the air valve valve timing.In addition, be in universal time coordinated at crankshaft and piston, original dynamical balancing in each cylinder can be destroyed or lower to the process that changes phase relationship between the piston.
The objective of the invention is to solve problems of the prior art, a kind of two stroke engine is provided, it can adapt to different working conditions, and the valve to motor in an adjustment range wideer than prior art carries out the timing adjusting.
According to the present invention, what be realized is, internal combustion engine distribution timing is regulated the position that the difficulty that is run into is porting, and/or the position between corresponding air valve, can destroy or lower original dynamical balancing in each cylinder particularly in the process of phase relationship between most.
Japan Patent JP57-102515 discloses a kind of two stroke engine, and the timing of porting is controlled in suggestion changeably with respect to piston.But its suction port and relief opening are the end in the working room basically, almost radially relatively settle in a usual manner.This structure can only change the cross-section area of porting, and can not control the timing of porting with respect to crankshaft ﹠ connecting respectively and independently.In addition, control unit is rotating sleeve, just changes the cross-section area of porting, and can not fully close porting.
The objective of the invention is to solve problems of the prior art, a kind of two stroke engine is provided, it can adapt to different working conditions, and the valve to motor in an adjustment range wideer than prior art carries out the timing adjusting.
For realizing above-mentioned purpose of the present invention, the invention provides a kind of reciprocating engine that is applicable to two stroke engine, comprise the mechanism that limits the working room; The piston mechanism of the firing chamber that can be back and forth in the working room changes with defined volume; Connect with piston mechanism and be suitable for to-and-fro motion with piston mechanism and be converted to rotatablely move and maybe will rotate the moving reciprocating replaceable switching mechanism that converts to; The suction port and the relief opening that are used for the firing chamber, suction port and relief opening are placed in or close each end, firing chamber; The valve mechanism that is used for above-mentioned suction port and relief opening; The controlling mechanism of the valve timing relation between the displacement of adjusting switching mechanism and valve mechanism, according to the present invention, described valve mechanism is made of the valve mechanism that is used for above-mentioned porting separately, and these valve mechanisms are different from above-mentioned piston mechanism; Have at least a valve mechanism to be included in the above-mentioned working room and be used as reciprocating guiding valve around above-mentioned piston mechanism; Make above-mentioned each valve mechanism shuttling movement with the above-mentioned reciprocating device of response piston; Described adjusting cooperates that the controlling mechanism of gas timing relation comprises the timing bent axle, links to each other with described guiding valve and drive the driving mechanism of guiding valve, the driving mechanism that this driving mechanism and timing bent axle are coupled together and the device of regulating described driving mechanism phase place, described timing controlling mechanism can be regulated respectively the relation of the valve timing between the displacement of the shuttling movement of each valve mechanism and switching mechanism, thereby regulates the timing relation between each valve mechanism shuttling movement.
Adopt the present invention, just might be given in the unrestricted basically variation of valve timing in the wide scope, this is because the spacing of porting can more accurately be controlled the intake and exhaust flow, and if desired, can realize substantially that the channelling of not having back fully of intake and exhaust is moved.In addition, or near the working room separately the valve train that separates of end avoided the danger of their phase percussion, certainly, percussion danger between this piston and one of them valve train can be alleviated by certain measure, as utilizes other valve train that is in full adjusting to carry out little to above-mentioned valve train or do not add the valve train of a class as guiding valve of regulating or utilizing an above-mentioned unlikely generation percussion.In general, the present invention is applicable to the combination of all kinds valve train, comprising guiding valve, poppet valve and revolution distributing valve, and air inlet and exhaust valve mechanism preferably can both carry out the valve timing adjusting, and the motor embodiment that the present invention is easy to adopt is that cylinder head has the casing wall of exhaust poppet valve and close lower dead centre that special rood (Detroit) diesel engine of moral and Lv Kaduo (Ricardo) slide valve engine of some suction ports are arranged.
The unconfined substantially change in a wide scope of air inlet and exhaust valve valve timing makes the air inlet timing, and exhaust timing, effective compression ratio, effective expansion ratio, toxic emission process and pressurization all significant variation can take place.This excursion makes the characteristic of this reciprocating engine that total change can take place, and for example, the characteristic that the low-power motor of the family expenses sedan car that travels in characteristic of using from racing car that motor had and road is had all can change.Its advantage is that the air valve valve timing can regulate by double-cam, eccentric wheel and/or other suitable operating device in operation process, can not only continuously and can realize changing valve timing in each circulation.
We adopt term " effective compression ratio " be meant when the working room in a cyclic process, reach this volume constantly of sealing divided by this cyclic process in the minimum volume of working room, and " effectively expansion ratio " this term is meant when the working room and has just begun to open volume when carrying out exhaust divided by the minimum volume of working room in this cyclic process in a cyclic process.
An outstanding advantage of the present invention is to make two stroke engine and pressurized machine realize optimized the joint in the advantage aspect the accurate one control air valve valve timing ability particularly.The relevant benefit of pressurized machine is well-known, and it has obtained successful for many years application in four stroke engine.Yet, pressurized machine can successfully be applied to be it is believed that it is very difficult on the two stroke engine.This is because motor requirement manifold suction pressure is the cube function relation of speed rises to a great extent, and this is that the exhaust pressure characteristic extremely different with pressurized machine is conflicting.Be because two stroke engine can not have abiogenous completely aspirating stroke the four stroke engine of elephant in addition.
These problems have all run in the present invention.The technical measures of regulating between two valve trains make following two noticeable interim valve timings relations become possibility:
(i) when needs carry out hot exposure again, outlet valve is early opened the pressure that can utilize residual gas in the cylinder and/or heat energy and/or kinetic energy and is driven pressurized machine, thereby is easy to the circulation of air inlet again.
(ii) to the starting generally except that cold especially weather, valve timing can be adjusted to and cause compression ratio to improve in order to starting, again compression ratio is turned down after working together.
In general, valve train will be driven by switching mechanism, and switching mechanism can comprise one or more bent axles, and driving mechanism can comprise an internal tooth driving belt or a gear transmission chain that is commonly referred to as synchronous band, stub and pin or eccentric wheel and follower.In most preferred embodiment, the driving mechanism of regulating air valve includes a helical gear Transmitted chains, and controlling mechanism includes the mechanism that changes the gear transmission chain phase place.The gear transmission chain of regulating air valve can comprise be contained in the switching mechanism and the air valve live axle on helical gear separately, the oblique gear mechanism that is inserted into meshes with described helical gear, its oblique gear mechanism is parallel to helical gear shaft and moves linearly.
In the internal-combustion engine in early days, the technical barrier that poppet valve runs into is excessive noise and is easy to produce pinking and catches fire in early days.What replace poppet valve is guiding valve, and it is adopted in the motor of a large amount of early stage commercial usefulness, particularly aeroengine.The development history of slide valve engine is blocked be entitled as in " high speed internal combustion engine development " book (by London Bu Laikexun Co., Ltd published) write Lu Halley more and has been made good general introduction.Halley Lv Kaduo has manufactured and designed many successful long slide valve engines of life-span, and this motor has been carried out performance study and optimized design widely.
Slide valve engine has a lot of outstanding advantages, and its mechanical efficiency and fuel consume leave deep impression to the people, and wherein the friction loss that friction causes between the reciprocating sleeve of being made by nitriding steel and cylinder sleeve and the piston is beyond thought low.If sleeve with circumferentially all reciprocating, just has extremely good lubricating condition vertically between sleeve and cylinder sleeve.This Lu blocks that many slide valve engines can move a lot of hours and sleeve and piston motion serious problems can not occur.This engine mildness and the piston temperature of discovery in the liquid cooling slide valve engine are to hang down a bit than the poppet valve motor outline of same capacity and output power.Obviously, this is to pass away because of the heat of moving oil film between sleeve and the cylinder sleeve with piston, and oil film becomes effective convection heat exchange body.Because cylinder head is not subjected to the obstruction of the gentle valve of gas port, people just are not subjected to any restriction when the shape of considering the firing chamber and displacement volume.
These advantages are particularly suitables to two stroke engine, but find yet that some hinder the remarkable shortcoming that two-stroke slide valve engines can not the wide range of commercial application, promote in early days particularly that valve type engine exists and the bad performance that solved afterwards.Lu blocks and has seen more, and states the summary of having made following two important technology difficult problems in the 387th page of the works quoted thereon:
" 1. the nitriding steel sleeve may wear in the top and can not be approximately 2000 to 4000 hours with working life before.This has been a long enough to military aero-engine, but is not enough to the motor that common commercial is used.Must take some measures and reduce this a part of rate of depreciation.”
Although " as if 2. open-ended jacket tube is all more perfect under all operating modes than the end enclosed type; during cold starting, can not realize sealing fully, must take some measure; as spraying low-viscosity oil, to realize the ignition by compression of cold starting: this is a quite bad characteristic.”
The wearing and tearing on sleeve top are to be exposed among the exhaust fully and/or the mechanical friction on cylinder sleeve or cylinder head top causes because of this part.Second shortcoming of slide valve engine is that the huge and expensive cavity type cylinder head that is commonly referred to as cylinder head is arranged, because increased heat loss, it is difficult will fully cooling off under air cooled situation.
In the four-stroke slide valve engine, Lu blocks two technical barriers noticing and not obvious more, but huge and expensive cylinder head remains and reaches a commercial important obstacle.
Not by Lu block repay knowledge in british patent specification 497, in 300 by Bock graceful (Porkman) and in B. P. 1,015, in 189 be by the disclosed a kind of technological scheme that solves these technical problems of Lin Dese (Lindsay), adopt the basic principle of guiding valve and opposed piston type engine, a kind of paired opposed pistons is provided, and its ferrule configuration separately has the required air valve of porting.That succeed and can the opposed piston type engine of commercial purposes in representative instance be you of Junkere phase nine not (Junkevs Jumo) and Roots (Roots) diesel engine and by Pierre's Dare Dick (NapierDeltic) motor, but all these depends on the piston one control air valve.Up to the present, the claimant is clear that, the opposed piston type engine that Bock is graceful or Lin Dese is designed is definitely can not be commercial, although and slide valve engine has the pointed advantage of Lv Kaduo, after the World War II also as just history relic.Yet what can put letter is, the present invention will impel the realization of these advantages, no matter opposed the or opposed piston engine of right and wrong.
A kind of slide valve engine of now concrete research, sleeve preferably not only can be vertically but also can be circumferentially reciprocating.Circumferential reciprocating stroke preferably is at least 20% of vertical to-and-fro motion stroke.
Two opposed pistons are arranged in the working room, and the porting that is spaced apart from each other has guiding valve separately, this guiding valve is convenient to reciprocating motion of the pistons relatively separately.Two pistons preferably are furnished with bent axle separately, and the to-and-fro motion of sleeve is driven by the driving mechanism that separately bent axle separates.Preferably directly by the contact of internal tooth driving belt, the live axle of transfer charge preferably is parallel or coaxial connection with one of them bent axle to bent axle.
Suction port is convenient to be connected on the pressurized machine, and is more suitable for installing the exhaust-driven pressurized machine by discharging.
Reference is routine accompanying drawing down, by an example, further illustrates two embodiments of the present invention.
Fig. 1 is a schematic cross-section according to multiaxis two-stroke opposed piston slide valve engine of the present invention, and the piston shown in it is near upper dead center.
Fig. 2 is the enlarged view of Fig. 1 first half.
Fig. 3 is the sectional view that the first half of motor shown in Figure 2 is made into the motor of independent operating.
See figures.1.and.2, opposed pistons two stroke engine 8 is a symmetry fully with respect to section A-A wherein, and it has a cast engine block 9, and this body has a cylinder sleeve 12, limits a working room and covers 35 crankcase 14,15 with having.This motor also has crankshaft group 16,17 and a pair of opposed piston 18,19 that connects with crankshaft group 16,17 by connecting rod 20,21 separately, and opposed piston 18,19 can do relatively reciprocating motion in the working room, and by the internal tooth driving belt regularly.For convenience's sake, cylinder sleeve 12 and crankcase component 14,15 illustrate with an one piece casting.But they are can be according to circumstances different and change.Fig. 1 shows the inside annular groove that the bent axle that is under the same situation is positioned on the piston of upper dead center and the cylinder sleeve 12 gas port 26,27 separately.Bent axle certainly arranges by required phase place, for example, and for the phase place that reaches two stroke engine and have good ventilation to require is arranged bent axle.In the running, gas port 26,27 leads to annular manifold 25,29 separately, and annular manifold comprises an intake manifold and a gas exhaust manifold, communicates with pipeline 25a, 29a successively.The structure of these manifolds and associated pipeline is unspecified, and that only illustrates in the drawings shows.Admission line 25a links in the outlet of interior turbocharger assembly 90 with including the gas compressor 92 that turbine 94 drives, turbine 94 by the waste gas of discharging along pipeline 29a as power.
Crankcase is identical with crankshaft group basically, and therefore a first half structure to motor shown in Figure 1 gives detailed explanation, is amplified in Fig. 2.Crankshaft group 16 comprises the bent axle of a pair of coaxial line, and one is that live axle 40, two is timing bent axle 41.These two bent axles are installed in crankcase 14 and the crankcase cover 35 by the roller bearing 42,44 that separates each other.This crankshaft group basic setting type routinely connects with piston, comprising having a tubular crankpin 46, one to be contained in matching hole 51 in the piston 18 or wrist pin 50 and the connecting rod 20 in the transverse holes 51.Connecting rod 20 will be installed in separately the lining 54,55 by pivot pin 46 and wrist pin 50.
Two timing bent axles 41 are sufficient admittedly on the belt pulley separately 60,61 of timing driving belt (Fig. 1) by bent axle 40 usefulness keys.Shown in 40a, adopt the taper mating face can guarantee that not only assembling is reliable, and can make the timing driving belt not have tensioning under the counter pulley situation.
The to-and-fro motion of sleeve 10,11 is to be realized by independent helical teeth Transmitted chains 68 by bent axle 40 separately.The substantially identical and dosage of helical gear Transmitted chains have by sleeve regulate separately piston and the air valve of associated gas port between timing relation or phase place and then regulate mechanism according to timing relation between the sleeve of the present invention.Each gear transmission chain 68 has helical gear 72,73 separately on bent axle 41 and axle 74, these gears and 71 engagements of middle helical gear, gear 71 are installed on the stub 75 of an insertion and slidably also turn.Because described motor is two stroke, so the velocity ratio of gear 72,73 is 1: 1.
Axle 74 is installed among the roller bearing 74a and has the bearing support 76 of the ball bearing 78 that matches with protuberance 80 of packing into, and protuberance 80 is integral with sleeve and crosses out.Be understood that this layout has reached two kinds of needed motions, as mentioned above, if circumferential reciprocating stroke is no less than 20% of vertical to-and-fro motion stroke, so this motion is exactly optimized scheme for lubricating.
Phase adjusted is to realize by the sliding push-pull bar in the circular groove 81 that is configured in the boss 82 on the intermediate gear 71 77.Pull bar 77 passes gear box cover 79 and slidably: gear 71 one moves and will cause relatively rotating of each gear slightly along stub 75, because these gears all are helical gears, will cause the change of phase place between bent axle 40 and the axle 74, change timing relation recited above then.This layout can be carried out timing phase without restriction 180 ° of scopes and be regulated.
If need not drive each sleeve by axle 74, also can use a camshaft.This just provides a bonus, promptly changes the timing relation and not only can pass through pull bar 77, can also adopt the cam of a selected shape in each engine strokes.
Sleeve 10,11 is furnished with the complementary pit 32b that aims at jetburner 32 and piston groove 32a in required time.Gap 26a, 27a in the sleeve on request with 26,27 actings in conjunction of cylinder sleeve gas port.No longer need to consider to provide detail with the connected port configurations form of the phase characteristic scope aspect of motor roadability, air-flow and hope, the problem that the timing adjusting needs to consider under the relevant different load condition of motor also is well-known, because such regulation technology belongs to prior art.
A disclosed important optimum performance with motor of steady and failure-free operation is to be to adopt timing drivign belt 24 as the joiner that directly drives between the bent axle among Fig. 1 and Fig. 2.For the most suitable timing driving belt of this specific use is a kind of up-to-date timing driving belt that is designed by the HTD that You Liluoyeer company (Uni Royal Company) sells, and this band also is best suited for the connection of the output shaft of on-load.
The people is understood that, the motor described in Fig. 1 and Fig. 2 can be made other improvement according to its working method and engine design principle.For example, can adopt as the positive displacement of Kai Dunsi (Kadency) and/or routine and/or the centrifugal supercharger of mechanical type driving.The guiding valve air inlet principle of having set up can be at cylinder sleeve and sleeve, is applied between the piston ring of two kinds of motions of sleeve and the direct contact of nothing mutually and the cylinder sleeve gas port.
What will further understand is, above-mentioned Lu who quoted as proof blocks two major defects of two-stroke slide valve engine of pointing out more and can overcome: sleeve ends no longer includes owing to be exposed to the wearing and tearing that cause in the exhaust flow of discharge, lacks the problem of sealing when no longer including cold starting at the sleeve openings end.Motor sleeve outer end illustrated in figures 1 and 2 is in crankcase, thereby and inner is sealed by cylinder sleeve that neither be exposed in the blast air also need sealing when the starting.This just makes the characteristics that can effectively utilize slide valve engine, and compensation is in sleeve and steel-jacket gap size with pass through relation between this gap heat transfer rate automatically.For example, when the fit tolerance of cylinder sleeve and sleeve is big, prevented by oil film from the heat transmission of piston face.The transmission of this heat is to cause the thermal expansion of sleeve that the gap is reduced, and this phenomenon is till the heat dissipation rate of oil film and heat are determined to reach thermal equilibrium between the sleeve diameter.
In addition, the cancellation cylinder head means the eliminations expensive and parts that thermal loss is high.The parts that are not easy to air cooling that cause because of its big cavity have just been cancelled.For after a bit, be the air cooling problem that solves the cavity cylinder head, people can find enjoyably that Bristol airline (Bristol Aeroplane Company) once made cooling and the copper material cylinder head that detailed material mixture ratio is arranged of very expensive band.
With the guiding valve of opposed piston structural part as motor illustrated in figures 1 and 2, not only might overcome the remarkable shortcoming of slide valve engine, and concerning opposed piston type engine, many again important well-known advantages of slide valve engine, especially mechanical efficiency and burning have significant improvement with respect to existing opposed piston type engine, and power-weight ratio increases significantly.Therefore, in some application facet of closing chain, the shortcoming on the sort of tedious form structure of opposed piston type engine just can overcome, and makes its compact structure can obtain given output power again.
The timing relation that can change selectively between the piston of each sleeve and associated is to make the unconfined change in the scope of broad of effective compression ratio, expansion ratio, timing time and firing chamber swept volume become possibility.These change not only can become another circulation from a circulation, but also can impel control system to change sensitively by the needs of engine load in the change in each circulation.This adaptability is particularly advantageous to the operation of two stroke engine, and it is that compromise regularly the adjusting is opposite with the choosing of most conventional motor.This motor can be by the work that is complementary of a kind of simple driving mechanism and variable load moment.Thisly realize that by continuously changing the moment driving mechanism payload optimum Match can be replaced by engine application itself.The measure that the air inlet and exhaust valve 26 and 27 of motor is separated from each other has further advantage, and one of them is exactly that in fact not return channelling when effective compression ratio and/or expansion ratio change moving.This all is impossible to opposed piston type engine or the poppet valve motor with conventional air valve.
Provide the turbo charged two stroke engine of a kind of multipurpose to become possibility according to the technical solution of change air valve valve timing of the present invention is feasible.In general conventional two stroke engine is unsuitable for adopting pressurized machine, and turbosupercharger just still less.Even can be equipped with turbosupercharger, provide enough air inflows in the time of also can not leaning on it for engine start.Therefore, require a kind of independent mechanical supercharger for overcoming these deficiencies always.
Attempt to find under a kind of two stroke engine situation of being furnished with turbosupercharger people, require the mechanical compressor that has a kind of outside that is suitable for start request to separate always.
In contrast, the function of starting of the present invention makes two stroke engine adopt turbosupercharger to become possibility in the scope of whole service state, and has cancelled the outside mechanical compressor that separates.For example, when requiring hot exposure again, open relief opening ahead of time and utilize the pressure of residual gas in the cylinder and/or heat energy and/or kinetic energy to drive turbosupercharger to be beneficial to recirculation.For starting at ordinary times, the especially starting of cold weather, the valve timing that can regulate air inlet and exhaust valve improves compression ratio, reduces after the starting again.Under full load condition, the valve timing of change air inlet and exhaust valve overcomes the air inlet characteristic of motor and the incompatibility of the inherence between the turbosupercharger output characteristics is possible, in general, the main performance of motor is coordinated mutually.
Changing the firing chamber swept volume makes motor long time of operation under the mean effective pressure of the dynamometer indication with high thermal efficiency.In other words, the output master of motor is if it were not for its volume controls by improving, and the mean effective pressure away from effective status of dynamometer indication controls but improve.
What will be noted that is that above-mentioned layout can produce in each cylinder near the optimal first order and second level dynamical balancing.On the contrary, as mentioned above, anyly change between the piston method of phase relationship with attempt and regulate compression ratio and all can damage this high-caliber dynamical balancing.
Fig. 3 show motor shown in Figure 2 half done improvement and the motor of independent operating.Because the method for operation and Fig. 2 of motor 108 are basic identical, except that its difference, other parts no longer are described.
The improvement part of the body 9 among Fig. 3 is limited to porose 112 and 114 head of combustion chamber 110, is equipped with one in its mesopore with the sparger shown in 116 or spark plug and a poppet valve 118.This poppet valve is shown in an open position, and it can take any form in many existing structures.In addition, the driving mechanism of poppet valve 118 is not illustrated, and it can be a non-regulating type valve used in the general motor.As an alternative, this poppet valve 118 is preferably adjustable for its valve timing.This adjustability for example can be by british patent specification 2,109, and the device of being introduced in 858 provides.In addition, the controlling mechanism that is used for guiding valve 10 as described herein can be copied, and is fit to do the poppet valve driving mechanism.Axle 74 can be received on the camshaft by gear transmission chain or belt pulley, and this camshaft has eccentric mass to drive the bias voltage that poppet valve overcomes spring.Adjusting helical gear 71 can change the phase place of poppet valve.
Other remodeling that the described motor of Fig. 1 and Fig. 2 adopts and other advantages that have can be used on the motor 108.
Though the present invention is the narration made from reference to internal-combustion engine, relevant principle of the present invention is adoptable to other forms of reciprocating engine equally, for example pump or compressor.
Claims (12)
1. a reciprocating engine that is applicable to two stroke engine comprises the mechanism that limits the working room; The piston mechanism of the firing chamber that can be back and forth in the working room changes with defined volume; Connect with piston mechanism and be suitable for to-and-fro motion with piston mechanism and be converted to that rotatablely moving maybe will rotatablely move converts reciprocating replaceable switching mechanism to; The suction port and the relief opening that are used for the firing chamber, suction port and relief opening are placed in or close each end, firing chamber; The valve mechanism that is used for above-mentioned suction port and relief opening; The controlling mechanism of the valve timing relation between the displacement of adjusting switching mechanism and valve mechanism, it is characterized in that described valve mechanism (10,11) by being used for above-mentioned porting (26 separately, 27) valve mechanism (10,11) constitute, these valve mechanisms (10,11) are different from above-mentioned piston mechanism (18,19); Have at least a valve mechanism (10,11) to be included in the above-mentioned working room and be used as reciprocating guiding valve around above-mentioned piston mechanism; Make above-mentioned each valve mechanism (10,11) shuttling movement with the response above-mentioned reciprocating device of piston (68); Described adjusting cooperates that the controlling mechanism of gas timing relation comprises the timing bent axle, links to each other with described guiding valve and drive the driving mechanism of guiding valve, the driving mechanism that this driving mechanism and timing bent axle are coupled together and the device of regulating described driving mechanism phase place, described timing controlling mechanism can be to each valve mechanism (10,11) shuttling movement and switching mechanism (16,17) the valve timing relation between the displacement is regulated respectively, thereby regulate the timing relation between each valve mechanism (10,11) shuttling movement.
2. reciprocating engine according to claim 1, the valve train that it is characterized in that porting is by separately drive mechanism, this driving mechanism comprises a helical gear Transmitted chains, and described controlling mechanism comprises the mechanism that changes the phase angle by gear transmission chain.
3. reciprocating engine according to claim 2, the gear transmission chain that it is characterized in that described each valve train comprise in the switching mechanism that is contained in each piston and the live axle of valve train on helical gear separately, the oblique gear mechanism that inserts meshes with described helical gear, and described gear mechanism is parallel with described helical gear to be linear motion.
4. one kind according to claim 1 or 2 or 3 described reciprocating engines, and the connection that it is characterized in that described suction port will be accepted the gas from booster body.
5. reciprocating engine according to claim 4 is characterized in that the exhaust gas driven that described booster body is discharged by described relief opening and turbosupercharger is arranged.
6. one kind according to any one described reciprocating engine in the claim 1 to 3, it is characterized in that being provided with in the working room the separately guiding valve of a pair of reciprocating opposed piston and two relative reciprocating motions of the pistons.
7. one kind according to any one described reciprocating engine in the claim 1 to 3, it is characterized in that described two guiding valves that separate all pass through the boss that end separately is provided with, and drives reciprocating by separately driving mechanism.
8. a reciprocating engine according to claim 1 is characterized in that described switching mechanism directly drives connection by the internal gear driving belt.
9. reciprocating engine according to claim 7, it is characterized in that switching mechanism comprise two pistons bent axle separately with described two timing mechanisms that bent axle is connected.
10. a reciprocating engine according to claim 6 is characterized in that guiding valve can be arranged to longitudinally and circumferentially to-and-fro motion.
11. one kind according to any one described reciprocating engine in the claim 1 to 3, it is characterized in that the circumferential reciprocating stroke of each guiding valve is at least 20% of vertical to-and-fro motion stroke.
12. one kind according to any one described reciprocating engine in the claim 1 to 3, it is characterized in that also being included in the ignition mechanism of working in the described working room and makes this reciprocating engine become a kind of motor.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86106958 CN1033600C (en) | 1986-09-25 | 1986-09-25 | Reciprocatory machines |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 86106958 CN1033600C (en) | 1986-09-25 | 1986-09-25 | Reciprocatory machines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN86106958A CN86106958A (en) | 1988-04-06 |
| CN1033600C true CN1033600C (en) | 1996-12-18 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 86106958 Expired - Lifetime CN1033600C (en) | 1986-09-25 | 1986-09-25 | Reciprocatory machines |
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| Country | Link |
|---|---|
| CN (1) | CN1033600C (en) |
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| CN102926865A (en) * | 2011-11-05 | 2013-02-13 | 摩尔动力(北京)技术股份有限公司 | Opposed piston sliding cylinder separated gas distribution engine |
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| CN102094702B (en) * | 2011-01-26 | 2013-12-04 | 杨成元 | Novel four-stroke layered double-swirling combustion energy-saving internal-combustion engine with new air distribution mechanism |
| CN102155285B (en) * | 2011-01-26 | 2013-05-22 | 杨成元 | Novel four-stroke four-cylinder layered dual-vortex combustion energy-saving internal combustion engine with new gas distribution mechanism |
| GB2493260A (en) * | 2011-07-26 | 2013-01-30 | Ecomotors Internat Inc | Opposed piston engine with tumble flow in shaped combustion chamber |
| CN102852639A (en) * | 2011-08-19 | 2013-01-02 | 摩尔动力(北京)技术股份有限公司 | Opposed-piston engine |
| CN112796972A (en) * | 2020-12-31 | 2021-05-14 | 随州精成精密机械零部件有限公司 | Energy-saving environment-friendly reciprocating sewage pump with blocking prevention and strong drainage capacity |
-
1986
- 1986-09-25 CN CN 86106958 patent/CN1033600C/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102926865A (en) * | 2011-11-05 | 2013-02-13 | 摩尔动力(北京)技术股份有限公司 | Opposed piston sliding cylinder separated gas distribution engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN86106958A (en) | 1988-04-06 |
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