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26 巻, 171 号
選択された号の論文の28件中1～28を表示しています
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浅野 友一1960 年 26 巻 171 号 p. 1483-1484
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーPDF形式でダウンロード (425K) -
中山 泰熹1960 年 26 巻 171 号 p. 1485-1492
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーUsing 5 types of rounded nozzles, 24 types of cylindrical nozzles (l/d=0.799∼16.520, l : length, d : diameter) and 5 types of knife-edged orifices of 0.3mm to 1.2mm diameter, the discharge characteristics were investigated for Reynolds number from 550 to 10000, using distilled water and low-pressure air. The results are summarized : 1. Discharge coefficients, which were calculated the basis of experiments using distilled water and low-pressure air, fall on the same curves, if arranged by Reynolds number and l/d. 2. Discharge coefficients for each type of nozzle or orifice were collected and one experimental formula was worked out. 3. Downstream pressure of nozzle or orifice is reduced to a minimum at a position of about 1.2 times the pipe diameter and is recovered at about 5 times the pipe diameter. 4. Recovery rate of pressure is about 1.7m (m : area ratio) for rounded nozzle and 1.2m for others.抄録全体を表示PDF形式でダウンロード (912K) -
中山 泰熹1960 年 26 巻 171 号 p. 1493-1501
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThe discharge characteristics of orifice or nozzle for high-pressure type air-micrometer were investigated for pressure difference from 0.2kg/cm2 to 3.0kg/cm2 over a range of pressure ratio from 0.25 to 0.95. The experiment has revealed the following : 1. By plotting cε (c : discharge coefficient of incompressible fluid, ε : expansion factor) against the pressure ratio, using parameter l/d, a nearly linear relation was obtained. For rounded nozzle, cylindrical nozzle and knife-edged orifice, a change of flow regime occurs respectively at the pressure ratio of 0.53, 0.55, and 0.63. 2. The values of ε at a position where the pressure ratio equal 1 agree with discharge coefficients of incompressible fluid over so-called "limit of constancy" of Reynolds number. 3. Discharge coefficients of each type of nozzle and orifice were collected and one experimental formula was worked out for each. 4. Downstream pressure and temperature are recovered at a position respectively 5 times and 4 times the pipe diameter. 5. Recovery rate of pressure was nearly same as in 1st report.抄録全体を表示PDF形式でダウンロード (956K) -
下山 美徳, 星野 達郎1960 年 26 巻 171 号 p. 1501-1507
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーSince there are few reports on rectangular weirs when m=h/b (h : head, b : weir width) has comparatively large value, and further, the study on the influence of D (height of weir) has not yet been performed, the authors carry out experiments of weir in which the channel width B is 0.11∼0.72m, m=h/b≤2.4, D≒0.28m and ≒0.05m. The results obtained may be summarized as follows : 1) The coefficient of discharge c has its minimum value cmin. 2) According as the value B/b increase, cmin approaches to a certain constant value which is prescribed by the magnitude D. 3) The region of B/b in which the side contraction is perfectly performed is given by a function of h/ (h+D). 4) When the value B/b is somewhat large, the coefficient c does not change by the magnitude of D. When the value B/b is large, in the region of m larger than that at which cmin takes place, the influence of D to the coefficient c decreases as m increases.抄録全体を表示PDF形式でダウンロード (798K) -
鵜沢 高吉1960 年 26 巻 171 号 p. 1507-1514
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーMaking use of a theoretical formula which expresses approximately, under the consideration of viscosity, the relation of floating force F and the lift of the circular disc valve which has an overlap between valve disc and seat, the equation of motion on valve is established, and the condition of valve vibration is discussed by means of Routh's criterion. Then as an example, the vibration of a water-supply cock is studied. The results obtained reveal that, in case where the radius of valve disc is relatively larger, when compared with the radius of valve seat. the effective pressure P is high and ∂F/∂P is negative, a selfexcited vibration appears, if the lift of valve is smaller, and then chattering occurs owing to the disappearance of a restoring force, if the lift is higher. In order to stop the vibration, it is effective to make small the overlap of valve disc and seat.抄録全体を表示PDF形式でダウンロード (812K) -
山田 豊1960 年 26 巻 171 号 p. 1514-1522
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーIn the present paper, the resistance of flow through the labyrinth packing is experimentally studied, when the clearance is larger than that of 1st report. The feature of flow through the labyrinth is also observed by photographic method. Results obtained are as follows : 1) When the clearance (s) is about 0.1∼0.2 times as large as the groove breadth (B) and the flow is in the state of turbulent, the value of resistance coefficient λ reaches maximum. When the flow is laminar, the value of λ increases with the increase of the clearance and it approaches to the theoretical value calculated for co-axial cylinder without grooves. 2) The value of λ for turbulent flow becomes maximum, when the groove depth is about one-fourth of the groove breadth, but for laminar flow, it is independent of the groove depth. 3) For laminar flow, the value of λg·Re (λg : coefficient of resistance in the groove, Re : Reynolds number) depends only on the value of s/B. 4) By using above results, profile of labyrinth for maximum value of λ is determined.抄録全体を表示PDF形式でダウンロード (1134K) -
植松 時雄, 森川 敬信1960 年 26 巻 171 号 p. 1522-1527
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーFrom the distribution of solids in the horizontal pipe the authors have deduced a result that the rate of fall of granular solids in the turbulent flow is smaller than the flow fluctuation, which approves the suspension of solids in the flow. Owing to the mutual collision of solids and the collision of solids against the pipe wall, solids are not conveyed in a constant state, but in a perpetually varying state. When solids are conveyed in a horizontal pipe, the velocitv distribution of air is not symmetrical with respect to the pipe axis. The authors have expressed the asymmetrical velocity distribution of air in consideration of both the weight ratio of solids to air in flow and the friction velocity.抄録全体を表示PDF形式でダウンロード (865K) -
植松 時雄, 森川 敬信1960 年 26 巻 171 号 p. 1528-1535
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThe authors have examined experimentally the pressure loss in the pipe bends, in which granular solids are transported. In order to investigate the pressure losses an assumption has been made that the total pressure loss consists of the losees in the flow of ordinary fluids through a pipe bend and those due to solids. It has been shown that the former is presented by the known formula and the authors have obtained the tact that the pressure losses due to solids increases in proportion to the weight ratio of solids to air in flow. Moreover the flow of solids in glass pipe bends has been observed. The observation has helped us in taking account of the effect of solids flow upon the pressure losses due to solids.抄録全体を表示PDF形式でダウンロード (944K) -
倉林 俊雄1960 年 26 巻 171 号 p. 1536-1542
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーIn order to develop the results obtained in the preveous reports in which only the water was used as the spraying liquid, the experiments were carried out on the solutions of glycerine and ethyl alcohol with viscosity ranging from 10 to 130 mP and with surface tension from 30 to 70 dyne/cm. The following conclusions were drawn : (1) When the rotating speed is low enough to form a continuous liquid jet, an increase in liquid viscosity up to μc=20∼40mP causes a decrease in the mean droplet diameter. The reason lies in an elongation of the continuous liquid jet. (2) In the state of spray the effect of viscosity on the droplet size becomes negligibly small. (3) The sizes of droplets can be reduced by decreasing surface tension in the whole range of the speed of rotation. (4) An empirical formula giving Sauter mean diameter d (μ) was derived in the spray region as follows : d=4.32×103 (σ/ρ) 0.25/υ1.15 where σ=surface tension (dyn/cm), ρ=density (g/cm3) and υ=resultant velocity of the peripheral and the discharge velocitiy (m/s). (5) As shown in Fig. 15, the relation between the maximum diameter dmax and the mean diameter d, that is, dmax≒2d is not influenced by the physical properties of the liquids.抄録全体を表示PDF形式でダウンロード (849K) -
倉林 俊雄1960 年 26 巻 171 号 p. 1543-1549
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーIn this paper the relationship between the droplet sizes and the frequency of their occurrences is investigated experimentally, giving consideration to the disintegration mechanisms of the jet. Fig. 1 shows the change of the frequency curve with increasing speed of rotation n. In this Fig., (a) and (b) correspond to the wavy jet and have two peaks of the frequency. The second lower peak moves towards the side of smaller size as the value of n increases. (d) ∼ (f) correspond to the partially sprayed jet. Since the jet is locally accompanied by the film-like disruptions, the number of the medium sized droplets is increased. In the spray the frequency curve becomes monotonous as shown in Fig. 4, and can be expressed by a formula dn/dx=ax2ebx where n is the number of droplets with diameter of x, and a and b are the constants. This formula is valid regardless the physical properties of liquid.抄録全体を表示PDF形式でダウンロード (716K) -
岸岡 英太郎1960 年 26 巻 171 号 p. 1549-1559
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThe methods usually applied to the analysis of potential flow in the radial type hydraulic machinery, such as those by Busemann and Fujimoto, were exclusively conformal transformation of vane-profiles onto a unit-circle and representation of potential functions by expansion in series. Where as the present author, beginning with some consideration upon the construction of complex velocity function for "displacement flow" through the radial straight vanes in rotation, has found that it must be expressed in a strict form of some Abelian integral. Then he has succeeded in deducing a generalized integral expression applicable to any type of vanes which can be conformally represented to the former ones. This paper comprises all these fundamentals and also his theory of obliquely radial vanes and its numerical results.抄録全体を表示PDF形式でダウンロード (1070K) -
岸岡 英太郎1960 年 26 巻 171 号 p. 1560-1569
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThis paper deals with the general principle of conformally transforming two circles onto two segments or double-row segment lattice, based on the idea that the function for representation will be given by a general expression applicable to the circles situated outside each other or osculating or intersecting each other. The functions are uniformly composed of all the elements of the infinite group of inversion with respect to each circle by a simple rule. The structures of the functions are simplified by some transformation to rearrange their poles at periodic points. Then the double wings are represented by the elliptic function of the second kind. The foregoing principle applies to the double-row lattice. Finally the performances of the Vee-wing lattice are deduced.抄録全体を表示PDF形式でダウンロード (884K) -
藤江 邦男1960 年 26 巻 171 号 p. 1570-1580
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーA blade of rotor with the type NACA-64 was tested with a low-speed test blower. Certain special techniques were applied to the measurements of the blow condition, namely, the measurements of pressure distribution on rotating blades and the measurement using a yaw meter which rotates with the rotor, etc. The measured blade-element performance was compared with the performace estimated from cascade data over a broad range of the incidence angles. As a result of this investigation, the turning and deviation angles of the rotor were found to agree with cascade data in the region of the annulus free from wall boundary-layer effects. The wake from upstream of the rotor causes the separation of the flow on the blade surface at a flow rate larger than the undisturbed flow. When the wake goes out through the rotor, the low-energy air of the wake experiences a greater turning than that of the main stream.抄録全体を表示PDF形式でダウンロード (1451K) -
原 朝茂1960 年 26 巻 171 号 p. 1581-1586
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーWhen a train enters into a tunnel, at first the pressure of the air immediately before the train head rises and the portion of the air with raised pressure spreads forward with a velocity nearly equal to that of sound. In other words the wave front, the boundary surface between the undisturbed air and the compressed air, moves forward, is reflected at the exit of the tunnel and comes back to the train head. In the present paper the aerodynamic phenomena, during the time interval from the instant of the train head entering into the tunnel to the instant either its tail end coming into the tunnel or the wave front being reflected back to its head, whichever occurs earlier, are treated theoretically. The air is assumed to be compreesible and inviscid. The velocities and pressures of air in each portion of the tunnel are calculated. The pressure drag of the train is also obtained. It is interesting to note that the effect of compressibility of air is remarkable in spite of a comparatively low speed of train.抄録全体を表示PDF形式でダウンロード (704K) -
竹矢 一雄1960 年 26 巻 171 号 p. 1587-1598
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーGenerally speaking up to the present time, the calculation of flow pattern of the axial-flow compressor has been treated on an assumption that the stream line is on the cylindrical surface with a rotating axis, but if the change of the passage area were big, the stream line would not incline nor curve with respect to the axis. For such a case, it is assumed that the inclination and curvature of the stream line are determined by the respective inclination angle and radius of curvature of the outer and inner walls of the flow passage. The present paper gives a practical solution for the assumption mentioned above.抄録全体を表示PDF形式でダウンロード (1047K) -
高田 浩之, 岡崎 卓郎1960 年 26 巻 171 号 p. 1598-1609
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーA theoretical method of calculating the propagating speed of the stall cells and the condition of the onset of the rotating stall in multistage axial compressors is given. Two fundamental limitations are, firstly, that the pitch (but not necessarily the chord) of each blade row must be small compared with the wave length of the stall cell (so called actuator disc theory), and secondly, that the disturbance must be small enough to allow the linearizing assumptions. The main conclusions are as follows : (1) In multistage compressors, the propagating speed is much influenced by the distance between the blade rows, the chord length of blades, and the time lag of the boundary layer. (2) The condition of the onset of rotating stall in multistage compressors is also given. The axial distance between blade rows and the time lag of the boundary layer have some influence while the chord length has not.抄録全体を表示PDF形式でダウンロード (1235K) -
高田 浩之, 岡崎 卓郎1960 年 26 巻 171 号 p. 1609-1621
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThe effect of the axial distance is examined closely by the theory presented in the 1st report. A criterion whether the stall cells of a shorter or a longer wave length are likely to occur is derived. The results of calculations are compared with the experiments of many investigations and agree fairly well, although the linearizing assumptions are far from real in many cases. The effect of the axial distance found by G. Sovran is well predicted by this theory. The experiments conducted by one of the authors at the Aeronautical Research Institute also confirm these predictions.抄録全体を表示PDF形式でダウンロード (1296K) -
小松 安雄1960 年 26 巻 171 号 p. 1622-1634
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーA new virial equation of state for ammonia was obtained. The second and the third coefficients of the equation were determined, using the experimental results of Beattie and Meyers, and the values that were calculated with the molecular theory by Rowlinson were adopted as the second virial coefficient for low temperature. A formula for specific heat of vapour ammonia under the ideal state was obtained, using the values that were calculated by Harrison and Kobe. A formula of vapour pressure of ammonia was obtained for a temperature range from -70°C to the critical temperature, using the experimental results of Cragoe and the others. The other charactaristic equations were made through thermodynamical calculation. The author calculated the charactaristic values of ammonia from the equation of state and the others, and made i-log10P diagram for a temperature range from 0.2kg/cm2 to 80kg/cm2 and also for a temperature range from -60°C to 300°C.抄録全体を表示PDF形式でダウンロード (1595K) -
牧 忠, 森本 隆雄1960 年 26 巻 171 号 p. 1635-1640
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーExtraction of oil and grease from oily and greasy substances is performed usually by means of heating and cooling cyclic phase-change of solvent. Instead of this method, the mechanical compression and expansion cyclic phase-change of solvent can be adopted, it thermodynamically and chemically adequate solvent is available. The characteristics of the latter cycle is discussed, and it is theoretically proved that the latter is more economical than the former and that the performance coefficient of the cycle is almost independent of the kind of solvent (working substance).抄録全体を表示PDF形式でダウンロード (733K) -
中村 行三, 中谷 洵1960 年 26 巻 171 号 p. 1640-1644
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーWe have been studying experimentally the heat transmission characteristics of our tubes of a new type in the case of air flowing across the bundles of tubes, and have already reported a portion of the results four times. Putting together all the results of our researches, we obtained the design data of the heat exchanger which consists of our new heat transmitting tubes. The main design formulas are as follows : 1) The heat transfer coefficient of Ist tubes in staggered arrangement for ratios p1/d=p2/d=2.11 is given by the equation Nu=0.602Re0.527, in which p1 is the longitudinal pitch of tubes and p2 is the transverse pitch of tubes, d is the outer diameter of tube, and Re is Reynolds number calculated with the maximum velocity between the tubes. 2) The pressure loss Δp of air flow through the bundle is given by the equation Δp=nψγumax2/2g, in which n is the number of tube rowas in flow direction, γ is the specific weight of the air, and umax is the maximum velocity that occurs between the tubes. The coefficient of resistance ψ may be obtained from the equation ψ=2.81Re-0.224.抄録全体を表示PDF形式でダウンロード (670K) -
菅原 菅雄, 吉川 進三, 造田 恵市1960 年 26 巻 171 号 p. 1645-1652
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーBy measuring the weight of a carbon globule hanged in a hot gas stream with a precise balance, the combustion rate of a carbon globule was determined and the temperature of the carbon globule was measured with an optical pyrometer. The conditions selected for the experiments were as follows : Concentration of oxygen in the gas stream co2=5.7, 15.6 and 21.0%. Initial diameter of the carbon globule 2ri=6.2, 8.9, 12.3 and 16.0mm. Velocity of the gas stream ug=5, 10, 15 and 20m/s. Temperature of the gas stream tg=800 and 900°C. By comparing the results of these investigations with those of the published theoretical analysis, it has been concluded that 1) the experimental results qualitatively agree with the theoretical ones in the every respect, 2) the combustion rate of a carbon globule changes proportionally to ug0.45 and (ri/r)0.46 in a gas stream containing 21.0% oxygen, 3) the combustion rate of a carbon globule changes nearly in proportion to co2/1.2, 4) with the decrement of oxygen contained in a gas stream, the effects of the velocity of gas stream and radius of a carbon globule on the combustion rate of the carbon globule decrease.抄録全体を表示PDF形式でダウンロード (1166K) -
田中 敬吉, 出原 清, 百合草 三佐雄1960 年 26 巻 171 号 p. 1652-1661
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThe thermodynamic properties of products of combustion corresponding to various fuel compositions are discussed, and it is concluded that their values depend almost only upon carbon-hydrogen ratios, and if the carbon-hydrogen ratio is held fixed, other constituents can be neglected. Next, the relation between the thermodynamic properties of products of combustion and the excess air factor n is discussed. It is proved that variables of state, such as entropy s, enthalpy i, specific heat cp, cv, adiabatic constant κ, etc., of the products of combustion vary almost linearly with 1/n. Utilizing this fact, the thermodynamic performance values of jet engines and gas turbines can be computed with great convenience. Thus, we propose approximate expressions for the thermodynamic properties of products of combustion in a linear form, i' (T, n) =i' (T, ∞) +iΔ' (T) · (1/n), s' (T, p, n) =s' (T, p, ∞) +sΔ' (T) · (1/n), ……, where i' (T, ∞), iΔ' (T), s' (T, p, ∞), sΔ' (T), ……, are independent of n, and determined under the conditions that the errors of these approximate expressions are held minimum.抄録全体を表示PDF形式でダウンロード (1312K) -
飯沼 一男, 山崎 毅六1960 年 26 巻 171 号 p. 1662-1667
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーSpontaneous ignition delay of fuel sprays injected into hot air in the temperature range from 250° to 900°C was measured at atmospheric pressure for various type of fuels. It is found that Arrhenius plot of the ignition delay is not linear but is bent at a temperature region from 600° to 700°C, and that the fluctuation in time lag becomes wider as the air temperature decreases. The effect of injection pressure, quantity of injected fuel and others upon the ignition delay was also studied, and it is understood that physical processes substantially rate the ignition at higher temperature and that chemical processes become important as the air temperature decreases. As a whole the values obtained are very similar to those determined by Mullins' flow method at higher temperature, and to those obtained by Moore's method at lower temperature.抄録全体を表示PDF形式でダウンロード (837K) -
福田 基一, 城戸 健一, 二村 忠元1960 年 26 巻 171 号 p. 1667-1675
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThe sound arresting effect against high sound of a muffler having sound absorbing walls was examined theoretically and experimentally. The experiments were also made to find sound arresting effects when the muffler has a mass of sound absorbing materials inwardly. As a result, it was found that the use of sound absorbing materials was very effective for the practical purpose, too. In that case the muffler was to be so constructed that the sound absorbing materials could be easily removable.抄録全体を表示PDF形式でダウンロード (1555K) -
長尾 不二夫, 嶋本 譲, 三宅 正毅1960 年 26 巻 171 号 p. 1675-1682
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーThe performance of an internal combustion engine is fairly well improved by the effects of the inlet and exhaust systems. The flow areas of those systems of the usual engine are not always suitable to make full use of the effects of the inlet and exhaust systems. The present authors have experimentally investigated the inlet system of a crankcase-scavenged two-cycle engine, which brings a most remarkable improvement to the delivery ratio. It has been confirmed that the delivery ratio increased by the effect of the induction pipe reaches maximum in the period of inlet port opening, which is longer than the usual period. Further they have examined the flow resistance of the carburetter and the air cleaner by replacing them with a throttle, and found out that the effect of the induction pipe is entirely vanished at the area-ratio of the throttle to the induction pipe under 0.3∼0.4.抄録全体を表示PDF形式でダウンロード (1029K) -
渡部 一郎, 安藤 亨, 仲田 哲朗1960 年 26 巻 171 号 p. 1683-1692
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーIn the previous paper, exhaust-pulsation of UD-3 engine having simple straight pipe exhaust system was experimented. The apparatus was identical with that descrived in the 1st report. In the present paper the influences of the exhaust pipe system having diffusers, nozzles, bends or elbows on the performance characteristic is reported. Results are as follows. a) For the case of exhaust pipe with diffusers, the pulsation coefficient for a straight pipe is available with the equivalent length derived from the impedance theory. Only a few percent increase in power was observed in comparison with straight pipe system in a favorable condition. b) For the nozzle, the pulsation effect can not be expected below an area ratio of 0.3, particularily in the case of a super-charged engine. From the view of an effective exhaust energy, a shorter pipe length is preferabl. c) The bend effect has little influence on the performance, judging from the pressure wave observations and the propagation velocity (dx/dt=u±c).抄録全体を表示PDF形式でダウンロード (1040K) -
東野 一郎1960 年 26 巻 171 号 p. 1693-1700
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーBy two new electronic methods…… (a) a digital method and (b) a gray wedge scope method……the propagation of the flame in the spark ignition engines is studied. Making use of the ionization gaps, the arrival of the flame front is detected, and how the flame travels in the combustion room can be made clear. These methods have an advantage that statistically enough data can be easily obtained. From the obtained shape of the timefrequency distribution curve for the arrival time ta, the progress of the propagation of flame is interpreted. In practical engine, a study on the irregularities in combustion caused by changing the setting direction of the ignition plug is carried out, and some interesting effects have been observed.抄録全体を表示PDF形式でダウンロード (972K) -
東野 一郎1960 年 26 巻 171 号 p. 1701-1707
発行日: 1960/11/25
公開日: 2008/03/28
ジャーナル フリーA new gas sampling valve working at high speed was prepared for the study of the scavenging in two-stroke engine, and its own performance was examined to obtain the basic data for the future design. This new valve is a kind of an electromagnetic solenoid valve, and it is actuated by making an instantaneous heavy current into a coil that generates an inverse magnetic field against the fixed magnetic field. The experiments were done to determine the working region of the valve, the time lag of the opening, the duration of valve opening and the volume of the sampled gas etc. AS a result, the time lag of for the opening td was about 0.5∼1.0 milliseconds, the duration of valve opening tf could be obtained for 1∼10 milliseconds and the gas could be sampled at a rate of about 10cc/ms under the pressure difference of 1kg/cm2.抄録全体を表示PDF形式でダウンロード (1000K)
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