WO2006080865A2 - Valve-timing gear - Google Patents
Valve-timing gear Download PDFInfo
- Publication number
- WO2006080865A2 WO2006080865A2 PCT/RU2005/000591 RU2005000591W WO2006080865A2 WO 2006080865 A2 WO2006080865 A2 WO 2006080865A2 RU 2005000591 W RU2005000591 W RU 2005000591W WO 2006080865 A2 WO2006080865 A2 WO 2006080865A2
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- WO
- WIPO (PCT)
- Prior art keywords
- valve
- shutter
- exhaust
- intake
- channel
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/28—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of coaxial valves; characterised by the provision of valves co-operating with both intake and exhaust ports
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/08—Shape of cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
- F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
- F01L3/205—Reed valves
Definitions
- the alleged invention relates to the field of engine manufacturing.
- Known valve timing mechanisms for internal combustion engines containing a common valve for intake and exhaust with inlet channels, inside of which are installed shutters with an actuator (for example, according to the application of Germany> fe 3812988, class FOlL 1/28). Its disadvantage is that a complex mechanical drive causes additional inertial loads and associated vibrations and reduces the reliability of the mechanism.
- a disadvantage of the known valve timing mechanism is that, as in the aforementioned, although to a lesser extent, when opening and closing the dampers, unbalanced inertial loads occur - moments of inertia, since the axis of rotation are made on one of their extreme sides, the moment of inertia with respect to which the greatest and overcoming of these moments of inertia forces may be on the verge of operability of the mechanism.
- the purpose of the invention is the reduction of unbalanced inertial loads, vibrations and energy consumption of the damper actuator.
- This goal is achieved by placing the axis of rotation of the shutter closer to the axis of symmetry, but with some ⁇ m offset relative to it to maintain the possibility of automatic opening under the influence of the difference pressure.
- a counterweight is made. It is necessary due to the fact that the shutters must rotate from closed to open and back at high angular speeds (up to 3000 times or more per minute), therefore they must be carefully balanced relative to the axis of rotation to reduce the inertial loads associated with this vibration and reduce the energy intensity of their drive.
- FIG. 1 shows a diagram of a valve timing for one engine cylinder.
- the valve mechanism contains a common valve with a plate 1, when opened, the engine cylinder (nadporshnevny space) 2 is connected to nadklapannym cavity 3, and through it with the open valve 4 - with the inlet channel 5 at the inlet stroke, or with the open valve 6 - with the exhaust channel 7 at a release stroke.
- the dampers are installed to separate the intake and exhaust processes. They form three isolated cavities: 1) the inlet channel, 2) the vypisky channel, and 3) the sealing cavity.
- the common valve opens under the action of two cams - 8 and 9 of the camshaft 10, through the beam 11 acting on the valve stem with plate 1 (the valve actuator can also be hydraulic, electromagnetic, etc.).
- the valve opens twice during the duty cycle (per revolution of the camshaft).
- the left (in Fig. 1) cam 8 camshaft serves to open the valve at the intake stroke, right 9 - at the exhaust stroke.
- the inlet flap 4 and the exhaust flap 6 isolate these channels from the nadklapanny cavity with the corresponding strokes.
- the rotation axes of the shutters are attached to them with an offset from the axis of symmetry (as in Fig. 1), which ensures the rotation of the shutters under the action of the gas pressure difference.
- vc- electromagnets 12 and 13 or stepper motors are installed, which guarantee their opening (with insufficient pressure difference) or fix their closed state at the command of the electronic engine control system (ECM - not shown in FIG. 1).
- balances 14 are made, moreover, they can be formed optionally in an explicit form, as in Fig. 1, and due to the thickening of the corresponding part, which avoids the occurrence of turbulent flows and an increase in resistance to the movement of gases.
- Other design options and the number of dampers and their actuators are possible.
- the mechanism works as follows (two versions of its operation), the first option - when working without pressurization of a gasoline or diesel engine, the supravalve cavity 3 is connected to the cylinder of the engine 2 (the over-piston space) when the valve 1 is opened - under the influence of the left cam 8 of the camshaft 10 the rocker 1 1 presses on the valve stem, lowering it with a plate 1 down. Under the influence of the pressure difference, the left shutter 4 opens (during the intake stroke), and the inlet channel 5 is connected to the cylinder of the engine 2 through the supravalve cavity 3. The air (or combustible mixture) is inlet. Subsequently, after completing the intake, compression, and stroke cycles, the exhaust gas exhaust cycle from the engine cylinder begins.
- the valve 1 opens under the action of the right cam 9 of the camshaft 10 and the rocker 1 i.
- the shutter 6 of the outlet channel 7 opens and the gases are removed, and the shutter 4 of the inlet channel 5 (in addition to the force of the spring 16) is pressed even more tightly against the sealing ledges 15 and is kept closed. Subsequently, the cycle repeats.
- the second option during the operation of an injection gasoline or diesel engine with supercharging even low overpressure (0.02 ... 0.03 MPa), the inlet flap 4 can remain open under this pressure constantly. In order to prevent leakage of charge air and maintain the required boost pressure, the inlet flap 4 of the inlet channel 5 must be blocked when the other strokes are closed, for example, by an electromagnet 12.
- Valve 1 opens and closes in the same manner as in the first embodiment.
- the exhaust gases from the cylinder 2 of the engine with the valve 1 open pass into the supravalve cavity 3, under their pressure, the valve 6 of the exhaust channel (when unlocked) opens and the gases are directed to the exhaust pipe (not shown in FIG. 1), In the following cycle repeats itself
- valve timing mechanism In the proposed valve timing mechanism, its operation occurs with less energy. The reduction of energy costs occurs due to the reduction of unbalanced inertia forces (as well as reducing the number of drive links). Vibration and wear of the damper drive parts are reduced. The reliability of the mechanism increases. Due to the indicated advantages (as well as the advantages of the general valve of the mechanism), high economic efficiency will be ensured.
Abstract
The invention relates to engine-building engineering. The inventive valve-timing gear comprises a common intake-exhaust disc valve (1) and intake (5) and exhaust (7) channels. A shutter (4) is arranged in the channel (5) and shutter (6) in mounted in the channel (7). Said shutters are used for dividing intake and exhaust processes. The rotation axis of each shutter (4, 6) is offset with respect to the symmetry axis. A counterweight (14) is embodied on each shutter on the side of offset. The inventive structural design makes it possible to reduce unbalanced inertia forces during the shutter motion, decrease vibrations, the drive wear and energy consumption.
Description
КЛАПАННЫЙ МЕХАНИЗМ ГАЗОРАСПРЕДЕЛЕНИЯ VALVE GAS DISTRIBUTION MECHANISM
Предполагаемое изобретение относится к области двигателестроения. Известны клапанные механизмы газораспределения для двигателей внутреннего сгорания, содержащие общий для впуска и выпуска клапан с подводящими каналами, внутри которых установлены заслонки с приводом (например, по заявке Германии >fe 3812988, кл. FOlL 1/28). Недостатком его является то, что сложный механический привод вызывает дополнительные инерционные нагрузки и связанные с ними вибрации и снижает надёжность механизма.The alleged invention relates to the field of engine manufacturing. Known valve timing mechanisms for internal combustion engines, containing a common valve for intake and exhaust with inlet channels, inside of which are installed shutters with an actuator (for example, according to the application of Germany> fe 3812988, class FOlL 1/28). Its disadvantage is that a complex mechanical drive causes additional inertial loads and associated vibrations and reduces the reliability of the mechanism.
Наиболее близким к изобретению по достигаемому результату является механизм газораспределения для двигателя внутреннего сгорания по ав- тппr.кпмv cP-wπe.тp.птчCτuv C1CfP ^i"0 ЯRЯR^fl кц FOl Г 1 /7 R ппvfш R 1 Q7ЯГ U котором заслонки выполнены автоматически открывающимися под действием разности давлений воздуха (горючей смеси) или отработанных газов.The closest to the invention on the attainable result is a valve mechanism for an internal combustion engine according to AB- tppr.kpmv cP-wπe.tp.ptchCτuv C 1 CfP ^ i "0 YARYAR KC ^ fl FOl T 1/7 R 1 R ppvfsh Q7YAG wherein U the shutters are made automatically opening under the action of the difference in air pressure (combustible mixture) or exhaust gases.
Недостатком известного клапанного механизма газораспределения является то, что как и в указанном ранее, хотя и в меньшей степени, при открывании-закрывании заслонок имеют место неуравновешенные инерционные нагрузки - моменты сил инерции, так как оси поворота выполнены на одной из крайних сторон их, момент инерции относительно которых наибольший и преодоление этих моментов сил инерции может оказаться на грани работоспособности механизма.A disadvantage of the known valve timing mechanism is that, as in the aforementioned, although to a lesser extent, when opening and closing the dampers, unbalanced inertial loads occur - moments of inertia, since the axis of rotation are made on one of their extreme sides, the moment of inertia with respect to which the greatest and overcoming of these moments of inertia forces may be on the verge of operability of the mechanism.
Цель изобретения - уменьшение неуравновешенных инерционных нагрузок, вибраций и энергоёмкости привода заслонок.The purpose of the invention is the reduction of unbalanced inertial loads, vibrations and energy consumption of the damper actuator.
Эта цель достигается путём размещения оси поворота заслонки ближе к оси симметрии, но с некоторμм смещением относительно её для сохранения возможности автоматического открывания под действием разности
давлений. Кроме того, для лучшего уравновешивания со стороны в которую от оси симметрии смещена ось поворота заслонки., выполнен противовес. Он необходим в связи с тем, что заслонки должны из закрытого состояния в открытое и обратно поворачиваться с большими угловыми скоростями (до 3000 раз и более в минуту), поэтому они относительно оси поворота должны быть тщательно уравновешены для уменьшения инерционных нагрузок, связанных с этим вибраций и снижения энергоёмкости их привода.This goal is achieved by placing the axis of rotation of the shutter closer to the axis of symmetry, but with some μm offset relative to it to maintain the possibility of automatic opening under the influence of the difference pressure. In addition, for better balancing from the side to which the axis of rotation of the damper is offset from the axis of symmetry., A counterweight is made. It is necessary due to the fact that the shutters must rotate from closed to open and back at high angular speeds (up to 3000 times or more per minute), therefore they must be carefully balanced relative to the axis of rotation to reduce the inertial loads associated with this vibration and reduce the energy intensity of their drive.
На фиг. 1 показана схема клапанного механизма газораспределения для одного цилиндра двигателя.In FIG. 1 shows a diagram of a valve timing for one engine cylinder.
Клапанный механизм содержит общий клапан с тарелкой 1, при открытии которого цилиндр двигателя (надпоршневое пространство) 2 соединяется с надклапанной полостью 3, а через неё при открытой заслонке 4 - со впускным каналом 5 при такте впуска, или при открытой заслонке 6 - с выпускным каналом 7 при такте выпуска. Заслонки установлены для разделения процессов впуска и выпуска. Они образуют три изолированных полости: 1) впускной канал, 2)выпycкнoй канал и 3)нaдклaпaянyю полость.The valve mechanism contains a common valve with a plate 1, when opened, the engine cylinder (nadporshnevny space) 2 is connected to nadklapannym cavity 3, and through it with the open valve 4 - with the inlet channel 5 at the inlet stroke, or with the open valve 6 - with the exhaust channel 7 at a release stroke. The dampers are installed to separate the intake and exhaust processes. They form three isolated cavities: 1) the inlet channel, 2) the vypisky channel, and 3) the sealing cavity.
Открывается общий клапан под действием двух кулачков - 8 и 9 распределительного вала 10, через коромысло 11 воздействующих на стержень клапана с тарелкой 1 (привод клапана может быть также гидравлическим, электромагнитным и др.). Клапан открывается дважды за рабочий цикл (за один оборот распределительного вала). Левый (по фиг. 1) кулачок 8 распредвала служит для открытия клапана при такте впуска, правый 9 — при такте выпуска. Заслонка 4 впускного канала и заслонка 6 выпускного канала изолируют эти каналы от надклапанной полости при соответствующих тактах. Оси поворота заслонок прикреплены к ним со смещением от оси симметрии (как на фиг. 1), что обеспечивает поворот заслонок под действием разности давления газов, В общем случае при соответствующем подборе параметров их крепления к оси поворота они могут открываться при любом скоростном режиме работы двигателя. Но для надёжности vс-
тановлены электромагниты 12 и 13 (или шаговые электродвигатели), которые гарантируют открытие их (при недостаточной разности давлений) или фиксируют их закрытое состояние по команде электронной системы управления двигателем (ЭСУД - на фиг, 1 не показана).The common valve opens under the action of two cams - 8 and 9 of the camshaft 10, through the beam 11 acting on the valve stem with plate 1 (the valve actuator can also be hydraulic, electromagnetic, etc.). The valve opens twice during the duty cycle (per revolution of the camshaft). The left (in Fig. 1) cam 8 camshaft serves to open the valve at the intake stroke, right 9 - at the exhaust stroke. The inlet flap 4 and the exhaust flap 6 isolate these channels from the nadklapanny cavity with the corresponding strokes. The rotation axes of the shutters are attached to them with an offset from the axis of symmetry (as in Fig. 1), which ensures the rotation of the shutters under the action of the gas pressure difference. In the general case, with the appropriate selection of the parameters of their fastening to the rotary axis, they can open at any high-speed engine operation mode . But for reliability, vc- electromagnets 12 and 13 (or stepper motors) are installed, which guarantee their opening (with insufficient pressure difference) or fix their closed state at the command of the electronic engine control system (ECM - not shown in FIG. 1).
Для уменьшения неуравновешенных инерционных нагрузок на заслонках выполнены противовесы 14, причём они могут быть сформированы необязательно в явной форме, как на рис. 1, а за счёт утолщения соответствующей части, что позволяет избежать возникновения турбулентных потоков и увеличения сопротивления движению газов. Возможны другие варианты конструкции и количества заслонок и их привода. Уступы 15 в стенках впускного и выпускного каналов., к которым с помощью возвратных пружин 16 и 17 прижаты заслонки, формируют уплотнение, достаточное для. изоляции полостей в этих, каналах от надклапанкой полости. Механизм работает следующим образом (два варианта его работы), Первый вариант - при работе без наддува бензинового или дизельного двигателя надклапанная полость 3 соединяется с цилиндром двигателя 2 (надпоршневым пространством) при открытии клапана 1 - под воздействием левого кулачка 8 распредвала 10 коромысло 1 1 давит на стержень клапана, опуская его с тарелкой 1 вниз. Под действием разности давлений открывается левая заслонка 4 (при такте впуска), и впускной канал 5 через надклапанную полость 3 соединяется с цилиндром двигателя 2. Происходит впуск воздуха (или горючей смеси). В дальнейшем после выполнения тактов впуска, сжатия и рабочего хода начинается такт выпуска отработанных газов из цилиндра двигателя. Клапан 1 открывается под действием правого кулачка 9 распредвала 10 и коромысла 1 i . Под давлением отработанных газов заслонка 6 выпускного канала 7 открывается, и газы удаляются, а заслонка 4 впускного канала 5 (дополнительно к усилию пружины 16) ещё плотнее прижимается к уплотнительным уступам 15 и удерживается в закрытом состоянии. В дальнейшем цикл повторяется.
Второй вариант — при работе впрыскового бензинового или дизельного двигателя с наддувом даже низкого избыточного давления (0,02...0.03 МП а) заслонка 4 впускного канала может остаться открытой под действием этого давления постоянно. Для предотвращения утечки наддувочного воздуха и поддержания требуемого давления наддува заслонка 4 впускного канала 5 при других тактах должна быть заблокирована в закрытом состоянии, например, электромагнитом 12. А для предотвращения открытия заслонки 6 выпускного канала под давлением наддува эта заслонка при такте впуска должна быть заблокирована в закрытом состоянии (например, электромагнитом 13). Клапан 1 открывается и закрывается в том же порядке, что и в первом варианте. При такте выпуска отработанные газы из цилиндра 2 двигателя при открытом клапане 1 проходят в надклапанную полость 3, под их давлением заслонка 6 выпускного канала (при разблокированном состоянии) открывается и газы направляются в выпускную трубу (на фиг, 1 не показана), В дальнейшем цикл повторяется,To reduce unbalanced inertial loads on the flaps, balances 14 are made, moreover, they can be formed optionally in an explicit form, as in Fig. 1, and due to the thickening of the corresponding part, which avoids the occurrence of turbulent flows and an increase in resistance to the movement of gases. Other design options and the number of dampers and their actuators are possible. The steps 15 in the walls of the inlet and outlet channels., To which the shutters are pressed by the return springs 16 and 17, form a seal sufficient for. isolation of cavities in these channels from the supravalve of the cavity. The mechanism works as follows (two versions of its operation), the first option - when working without pressurization of a gasoline or diesel engine, the supravalve cavity 3 is connected to the cylinder of the engine 2 (the over-piston space) when the valve 1 is opened - under the influence of the left cam 8 of the camshaft 10 the rocker 1 1 presses on the valve stem, lowering it with a plate 1 down. Under the influence of the pressure difference, the left shutter 4 opens (during the intake stroke), and the inlet channel 5 is connected to the cylinder of the engine 2 through the supravalve cavity 3. The air (or combustible mixture) is inlet. Subsequently, after completing the intake, compression, and stroke cycles, the exhaust gas exhaust cycle from the engine cylinder begins. The valve 1 opens under the action of the right cam 9 of the camshaft 10 and the rocker 1 i. Under the pressure of the exhaust gases, the shutter 6 of the outlet channel 7 opens and the gases are removed, and the shutter 4 of the inlet channel 5 (in addition to the force of the spring 16) is pressed even more tightly against the sealing ledges 15 and is kept closed. Subsequently, the cycle repeats. The second option - during the operation of an injection gasoline or diesel engine with supercharging even low overpressure (0.02 ... 0.03 MPa), the inlet flap 4 can remain open under this pressure constantly. In order to prevent leakage of charge air and maintain the required boost pressure, the inlet flap 4 of the inlet channel 5 must be blocked when the other strokes are closed, for example, by an electromagnet 12. And to prevent the opening of the exhaust flap 6 under the boost pressure, this flap should be blocked in the intake stroke closed state (for example, by an electromagnet 13). Valve 1 opens and closes in the same manner as in the first embodiment. At the exhaust stroke, the exhaust gases from the cylinder 2 of the engine with the valve 1 open pass into the supravalve cavity 3, under their pressure, the valve 6 of the exhaust channel (when unlocked) opens and the gases are directed to the exhaust pipe (not shown in FIG. 1), In the following cycle repeats itself
В предлагаемом клапанном механизме газораспределения работа его происходит с меньшими затратами энергии. Уменьшение затрат энергии происходит за счёт уменьшения неуравновешенных сил инерции (а также уменьшения количества приводных звеньев). Уменьшаются вибрации и износ деталей привода заслонок. Повышается надёжность работы механизма. За счёт указанных преимуществ, (а также преимуществ общего клапана механизма) будет обеспечена высокая экономическая эффективность.
In the proposed valve timing mechanism, its operation occurs with less energy. The reduction of energy costs occurs due to the reduction of unbalanced inertia forces (as well as reducing the number of drive links). Vibration and wear of the damper drive parts are reduced. The reliability of the mechanism increases. Due to the indicated advantages (as well as the advantages of the general valve of the mechanism), high economic efficiency will be ensured.
Claims
1. Клапанный механизм газораспределения двигателя внутреннего сгорания, содержащий общий для впуска и выпуска клапан с подводящими кaнa= лама, внутри которых установлены заслонки, вьшолненные автоматически открьшающимися под действием разности давлений, например, за счёт смещения оси поворота заслонок относительно их осей симметрии, отличающийся тем, что на заслошсах со стороны смещения выполнены противовесы. 1. The valve timing of the internal combustion engine, containing a valve common to the inlet and outlet with inlet channels = llama, inside which are installed dampers that are automatically opened by pressure difference, for example, due to the displacement of the axis of rotation of the dampers relative to their axis of symmetry, characterized in that on the flaps on the displacement side, counterweights are made.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| RU2005101511 | 2005-01-24 | ||
| RU2005101511/06A RU2286466C2 (en) | 2005-01-24 | 2005-01-24 | Valve-type timing gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| WO2006080865A2 true WO2006080865A2 (en) | 2006-08-03 |
| WO2006080865A3 WO2006080865A3 (en) | 2007-01-18 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/RU2005/000591 WO2006080865A2 (en) | 2005-01-24 | 2005-11-21 | Valve-timing gear |
Country Status (2)
| Country | Link |
|---|---|
| RU (1) | RU2286466C2 (en) |
| WO (1) | WO2006080865A2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GR20080100129A (en) * | 2008-02-29 | 2009-09-25 | Κωνσταντινος Δημητριου Θεοχαρης | Camshaft with cams of 180 and 90 degrees celcium and cylinder head with single input-output sleeve |
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|---|---|---|---|---|
| US2742028A (en) * | 1952-11-28 | 1956-04-17 | Jacob G Robinson | Valve mechanism |
| SU985627A1 (en) * | 1981-08-06 | 1982-12-30 | Проектно-Конструкторское Бюро Треста "Сантехдеталь" Главпромвентиляции Минмонтажспецстроя Ссср | Air valve |
| DE3520872A1 (en) * | 1985-06-11 | 1986-12-11 | Wiho 2161 Twielenfleth Stümpel | Method for reducing the wear of control devices in internal combustion engines and device for performing the method |
| SU1314207A1 (en) * | 1985-07-04 | 1987-05-30 | Предприятие П/Я Г-4941 | Device for removing internal combustion engine exhaust gases |
| DE4105848C1 (en) * | 1991-02-25 | 1992-08-06 | Franz 7069 Berglen De Rupp | Four-stroke IC engine with single cylinder valve - has secondary valves open during piston compression and work strokes |
| RU2154215C2 (en) * | 1995-04-28 | 2000-08-10 | Моника Пашковска | Thermodynamic suction valve |
-
2005
- 2005-01-24 RU RU2005101511/06A patent/RU2286466C2/en not_active IP Right Cessation
- 2005-11-21 WO PCT/RU2005/000591 patent/WO2006080865A2/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2742028A (en) * | 1952-11-28 | 1956-04-17 | Jacob G Robinson | Valve mechanism |
| SU985627A1 (en) * | 1981-08-06 | 1982-12-30 | Проектно-Конструкторское Бюро Треста "Сантехдеталь" Главпромвентиляции Минмонтажспецстроя Ссср | Air valve |
| DE3520872A1 (en) * | 1985-06-11 | 1986-12-11 | Wiho 2161 Twielenfleth Stümpel | Method for reducing the wear of control devices in internal combustion engines and device for performing the method |
| SU1314207A1 (en) * | 1985-07-04 | 1987-05-30 | Предприятие П/Я Г-4941 | Device for removing internal combustion engine exhaust gases |
| DE4105848C1 (en) * | 1991-02-25 | 1992-08-06 | Franz 7069 Berglen De Rupp | Four-stroke IC engine with single cylinder valve - has secondary valves open during piston compression and work strokes |
| RU2154215C2 (en) * | 1995-04-28 | 2000-08-10 | Моника Пашковска | Thermodynamic suction valve |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GR20080100129A (en) * | 2008-02-29 | 2009-09-25 | Κωνσταντινος Δημητριου Θεοχαρης | Camshaft with cams of 180 and 90 degrees celcium and cylinder head with single input-output sleeve |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2286466C2 (en) | 2006-10-27 |
| WO2006080865A3 (en) | 2007-01-18 |
| RU2005101511A (en) | 2006-07-10 |
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