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- TRANSACTIONS OF THE JAPAN SOCIETY OF MECHANICAL ENGINEERS Series C
- TRANSACTIONS OF THE JAPAN SOCIETY OF MECHANICAL ENGINEERS Series B
- TRANSACTIONS OF THE JAPAN SOCIETY OF MECHANICAL ENGINEERS Series A
- Transactions of the Japan Society of Mechanical Engineers Series C
- Transactions of the Japan Society of Mechanical Engineers Series B
- Transactions of the Japan Society of Mechanical Engineers Series A
Volume 9 (1943 - 1944･･･
- Issue 37-4 Pages 113-
- Issue 37-3 Pages 53-
- Issue 37-2 Pages 103-
- Issue 37-1 Pages 161-
- Issue 36-4 Pages 89-
- Issue 36-2 Pages 69-
- Issue 36-1 Pages 121-
- Issue 35-4 Pages 27-
- Issue 35-3 Pages 23-
- Issue 35-2 Pages 43-
- Issue 35-1 Pages 33-
- Issue 34-4 Pages 1-
- Issue 34-3 Pages 1-
- Issue 34-2 Pages 1-
- Issue 34-1 Pages 1-
Volume 8 (1942)
- Issue 33-4 Pages 215-
- Issue 33-3 Pages 33-
- Issue 33-2 Pages 63-
- Issue 33-1 Pages 185-
- Issue 32-4 Pages 185-
- Issue 32-3 Pages 21-
- Issue 32-2 Pages 53-
- Issue 32-1 Pages 117-
- Issue 31-4 Pages 101-
- Issue 31-3 Pages 1-
- Issue 31-2 Pages 25-
- Issue 31-1 Pages 43-
- Issue 30-4 Pages 1-
- Issue 30-2 Pages 1-
- Issue 30-1 Pages 1-
Volume 26, Issue 168
Displaying 1-23 of 23 articles from this issue
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Yoshiro KATTO1960 Volume 26 Issue 168 Pages 1047-1049
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSDownload PDF (610K) -
Shoju ITAYA, Yasuo YASUDA1960 Volume 26 Issue 168 Pages 1050-1053
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe frequency n of eddies generated behind a circular cylinder in fluid is expressed by the equation n=S (v/d), where v is the fluid velocity, d the diameter of circular cylinder and S Strouhal's number, which has been dealt with the function of Reynold's number. Many investigators have experimented on the values of Strouhal's number between Re≒3×10∼5×105, but the values between Re≒2×104∼1×105 have not been obtained. The present authors have experimented on all of them between Re≒6×10∼5×105 by three devices with high speed tunnel, low speed tunnel and water rotating vessel respectively and have made it clear that they take nearly a value of 0.18 between Re=1×104∼1×105 and suddenly increase 0.3∼0.6 at the point near the critical Reynold's number Rec≒5×105.View full abstractDownload PDF (571K) -
Iwao OKI, Kosaku KAWAKAMI1960 Volume 26 Issue 168 Pages 1053-1061
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThis paper presents the results of experiments on flat-seated valves with broader seat-face, discharging water into the air under a constant head of about 194 cm. Five valves were used in all, of which the first four had diameter d smaller than seat-face diameter d1 and the last one had d equal to d1. When the lift of the valves with d<d1 is gradually increased, the stream flowing out separates partially from the seat-face at a certain valve-lift, and then separates completely from the seat-face at a higher lift and becomes free jet. When the valve is closing the free jet finally clings to the seat-face at a very small valve-lift. These are represented by three special points on the characteristic curve of each valve. In case of the valve with d=d1, there are one separating and one clinging point on the curve, just as the valves with d>d1 on which we have already reported. We try to give some explanations for these phenomena hereunder.View full abstractDownload PDF (953K) -
Toshio TAKENAKA1960 Volume 26 Issue 168 Pages 1062-1068
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSDiaphragms are widely used as detectors of accumulators and manipulators of pneumaticautomatic control apparatus. The author measured the forces on diaphragms under a fluid pressure for each lift of valve, using diaphragms with several kinds of accumulators of lower and higher pressures, changing dimensions of discs and materials and sectional forms of diaphragms. As the results, for each diaphragm, the values of F/F0 concentrate on a straight line, regardless of the change of pressure, and are proportional to lifts. (F is the force which acts on the disc and F0 is a portion of the force that the diaphragm shares.) This tendency for the diaphragm is not changed by dimensions of the disc, but is changed by material and thickness of the diaphragm We explained the matter considering that inasmuch as the sectional forms of the diaphragms for each lift differ under a certain pressure, the directions of tensions of the diaphragm acting at boundary of the disc have an effect upon values of F/F0.View full abstractDownload PDF (802K) -
Tomitaro TOYOKURA1960 Volume 26 Issue 168 Pages 1069-1075
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe essential object of this paper is to know the reasons for the conspicuos increase of the head and brake horse-power of an axial-flow pump at low flow rates. In this report, the characteristics of pump, the flows before and behind the impeller blades and the pressure distributions on the casing wall near the impeller and guide vanes were measured. The results obtained are mainly as follows : 1. When the discharge becomes less than that begins the reverse flow on the suction side of impeller blades, the radial flow in the impeller increases suddenly, and the characteristics of pump change remarkably, too. 2. At that time, the casing wall gives an important effect upon the radial flow in the impeller and the angle between the rotational direction and the relative velocity of the fluid becomes larger than the discharge angle of runner blades near the casing on the delivery side of the impeller.View full abstractDownload PDF (1071K) -
Tomitaro TOYOKURA1960 Volume 26 Issue 168 Pages 1076-1083
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIn this paper, the flow in an axial-flow pump impeller at partial flow rates is studied by dividing it into two domains ; one is near the casing wall where the radial flow is seriously affected by the wall, another is far from it where the fluid flows a1ong impeller blades and an effect of the wall is negligibly small. By considering about the flow in impeller blades in this way, it becomes possible to analyse an impeller action and to demonstrate the reason for the conspicuous increase or the head at partia1 quantities. The analytical method to find the relation between the discharge and theoretical head is obtained. But a complexity of the flow makes it necessary to introduce some coefficients, which should be determined empirically.View full abstractDownload PDF (1025K) -
Tomitaro TOYOKURA1960 Volume 26 Issue 168 Pages 1084-1092
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIn order to obtain the data, which are necessary to find the values of coefficients introduced in the analytical solutions on the theoretical characteristics of axial-flow pumps, and to find the head loss at impeller blades, the velocity and energy distributions before and behind impeller blades, the pump characteristics and the pressure distributions on the casing wall near impeller blades are measured about 9 in vertical axial-flow pumps with the impellers of some different types. The results obtained are as follows. 1. The effects of the number of vanes, vane setting and vane profil on an impeller performance are discovered. 2. The width of a clearance between the impeller tips and the casing wall has little effects on an impeller performance at low flow rates.View full abstractDownload PDF (922K) -
Tomitaro TOYOKURA1960 Volume 26 Issue 168 Pages 1093-1101
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIn this paper, the values of some coefficients, which have been introduced in the theoretical analysis about the axial-flow pump performance shown in part 2 of this study, are determined by using the velocity distributions at the inlet and outlet from impeller blades obtained in part 3. These coefficients can be shown in comparatively simple forms, and an application of the theoretical solution to the actual problem becomes possible. In order to prove an accuracy of the theoretical solution, the flows before and behind the impeller blades and the theoretical head-flow characteristics of an axial-flow pump with impeller blades designed by the modified airfoi1 theory are calculated by using these coefficients. The results coincide considerably well with the experimental ones.View full abstractDownload PDF (1112K) -
Tomitaro TOYOKURA1960 Volume 26 Issue 168 Pages 1102-1110
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSBy using the experimental results shown in the previous reports, the writer treated the relation between the capacities and theoretical heads, and discussed the effects due to the types of impeller. The results obtained are as follows : 1. The hydraulic loss in impeller blades becomes maximum at critical discharge qc, and it has quite different tendencies before and behind qc. 2. In the axial flow domain (capacities larger than qc), the characteristics of an aerofoil section at the mean effective radius are derived for the mean flow at the inlet and outlet from impeller blades. It, thereafter, is found that the values of lift coefficients are in good agreement with the test data for the single airfoil for l/t≤0.8 (l : chord length, t : pitch), in spite of the change of setting angles and the number of blades. 3. In the centrifugal flow domain (capacities less than qc), the energy losses in impeller blades can be shown fairly well in comparatively simple forms.View full abstractDownload PDF (928K) -
Tomitaro TOYOKURA1960 Volume 26 Issue 168 Pages 1111-1120
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIn this paper, the following problems are discussed. 1. The discharge-head characteristics of an axial-flow pump are analysed empirically, and the coefficients of energy losses in guide vanes, suction and delivery pipes are determined. 2. Experimental studies are performed about the circulating flows on the suction and delivery sides of impeller blades of some different types, which affect seriously the shaft horse-power performance at low flow rates. The coefficients of head loss and the velocity coefficients of the circu1ating flow are derived in the same relation, regardless the different types of impellers. 3. Types of an axial-flow pump impeller which should have an excellent performance at partial capacities are estimated.View full abstractDownload PDF (1088K) -
Nishiro SAKURAI1960 Volume 26 Issue 168 Pages 1121-1125
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSUnder working condition, there happens an unusual high pressure rise at the guide vane entrance whenever the impeller blade tips pass the front of the guide vane passage. This unusual rise of pressure varies extremly according to existence or nonexistence of the cavitation in the pump. We analysed this phenomenon by means of Sulzer's experimental results which had been obtained by Siemens Oscillograph and then, we separated it into factors and attached theoretical meaning to it. We have made it clear that the only course of unusual pressure rise is the forced vibration of cavities in the turbine pump guide-vane entrance and differs of cavitation in infinite boundary as in the investigation reporeted by Knapp.View full abstractDownload PDF (647K) -
Fujio NAGAO, Shunichi OHIGASHI, Ichiro HIGASHINO1960 Volume 26 Issue 168 Pages 1127-1133
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSA fast response and sensitive resistance thermometer is studied which utilizes the "skin effect" and "resonance", provided that a radio frequency is used instead of direct current as a power source. A fine platinum wire (0.08 mm diameter) fed about 7Mc radio frequency current shows a character superior to that which is obtained by the customary method at the points of the response and the sensitivity. Also this method has an advantage to apply without decreasing the respose and the sensitivity, even if using a thick wire to obtain a mechanical strength. As a result, it will be useful for measuring the transient temperature change, for instance, a hot gas in the cylinders of the internal combustion engines and other similar cases.View full abstractDownload PDF (884K) -
Ikuo MABUCHI1960 Volume 26 Issue 168 Pages 1134-1138
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSAn approximate theory, accounted for the effects of both energy convection and fluid acceleration within the film condense layer, is reported in this paper and the similar method (Karman-Pohlhausen's method) to the heat transfer by free convection has been used also for the laminarfilm condensation on a vertical wall. Heat transfer results are expressed by the following simple equations and indicate a good agreement with the numerical exact solutions for special Prandtl numbers, which have been given by Sparrow and Gregg recently. (I) for high Prandtl numbers [numerical formula] (II) for low Prandtl numbers [numerical formula] where β is a functon of Prandtl number and of cΔT/hfg and is given by Figs. 2 and 3. The symbols used in the above equations are as follows : Nux : local Nusselt number, k : thermal conductivity, hfg : latent heat of condensation, c : specific heat, ΔT=Tsat-Tw ; Tsat : saturation temperature, Tw : wall temperature, g : acceleration due to gravity, ν : kinematic viscosity, ρ : condesate density, ρv : vapor density, x : distance measuring along wall from leading edge.View full abstractDownload PDF (630K) -
Katsuhisa MURAKAWA1960 Volume 26 Issue 168 Pages 1139-1143
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSFor the purpose of simple calculations by the Theory of Boundary Layer, the author performed the calculations of heat transfer of the case in which free convection and laminar flow coexist at the same time in the velocity entry length (entrance region) of the vertical double pipes with annular space (annulus) heated from the inner pipe. When the pipe wall temperatures are constant as usual, the treatments in the cases of laminar flow only and free convection only are comparatively easy. But, actually, there are many cases in which the pipe wall temperatures vary along the direction of the pipe axis, and free convection and forced 1aminar f1ow coexist at the same time. The author induced certain theoretical formulas for this case by the Theory of Boundary layer and the simple treatments as far as possible. The main points different from the usual methods in this thesis are : (1) The temperature distribution and the velocity distribution are shown by the Besse1 Functions, (2) f0 (z), the temperature distribution of the inner pipe wall is taken into consideration, and (3) Gauss' method of numerical integration is used. In the numerical calculations, we are able to avail Tables of Bessel Functions and Gauss' method with high accuracy and therefore it is very convenient in these respects. It has been revealed that the theoretical results coincide with the experimental results very well.View full abstractDownload PDF (733K) -
Atsushi SAIMA1960 Volume 26 Issue 168 Pages 1144-1150
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe blow-off of diffusion burner flames is affected by the shape of the burner tube, the flow pattern of mixture and surrounding secoundary air, and the state of concentration. There are three kinds of states of the blow-off of a diffusion flame. One is the state in which the mixture is in laminar flow. The other two states are those of turbulent flow. In the turbulent region of the mixture, a vortex of flame is created just outside of the burner tube. At a relatively low velocity of mixture flow in this region, the vortex of flame is blown away by the increasing of the surrounding secondary air velocity, and at a higher velocity of the mixture flow, the blow-off of the flame is accomplished by the blow-off of the propagation from the vortex of flame, as the velocity of secondary air increases.View full abstractDownload PDF (1067K) -
Kazuo IINUMA, Kiroku YAMAZAKI1960 Volume 26 Issue 168 Pages 1151-1159
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSSpark ignition of a fuel spray injected into the atmosphere from a Pintle nozzle has been studied, and it has been found that the ignitibility decreases almost linearly with the time after the end of injection, and that it decreases with increasing distance from the core of the spray cone. From these facts and theoretical considerations, it comes to the conclusion that the ignitibility depends on the total surface area of fuel drop1ets which disperse into a definite volume of air around the spark gap, and the ignition phenomena are found to be determined substantially by physical factors such as atomization and dispersion. Ignitibi1ity of a fuel spray by repeated sparks has been found to bear out the calculated results on the basis of probability considerations. In most cases, more volatile fuel is less ignitible by repeated sparks of the same frequency.View full abstractDownload PDF (1074K) -
Masami MINAMI, Seiya MUKOHARA1960 Volume 26 Issue 168 Pages 1160-1166
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIn order to make clear the effect of the cooling methods and of the flow quantity of oil on the piston temperature, the authors have measured some temperature distributions over the cast iron piston of a small engine, with some thermocouples. As the result of a series of experiments, the following conclusions have been reached : 1) In case of the jet cooling, there is a critical oil flow beyond which even if we may increase the quantity of oil flow we can not expect the decrease of the piston temperature. It is 1.5∼2.0 l/cm2/h with respect to the surface area of the piston. (For higher speed, greater quantity required.) 2) At the critical flow, the mean coefficient of heat transfer from the inside of the piston crown to oil is 1600∼1700 kcal/m2h°C. 3) In utilizing the oil jet from the nozzle located at the small-end of the connecting-rod, the mean coefficient of heat transfer approaches to the maximum local coefficient.View full abstractDownload PDF (897K) -
Motokazu FUKUDA1960 Volume 26 Issue 168 Pages 1167-1173
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe theoretical analysis of the exhaust muffler of an internal combustion engine contains various difficult factors. Almost all the studies on the attenuation characteristics of a muffler are an analysis based on the assumption that the tail tube is inhite in its length. But, from the practical point of view, the author considered the following points in order to induce a theoretica1 formula made to resemble the practical situation as closely as possible. a) The length of a tail tube is finite. b) The exhaust noise contains the sound radiated from the ejecting gas. c) The exhaust gases have some gradient in each exhaust system. On the other hand, he set some mufflers to an engine and conducted some experiments to compare the calculated value with the measured one.View full abstractDownload PDF (1059K) -
Motokazu FUKUDA1960 Volume 26 Issue 168 Pages 1174-1182
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIn the present paper, the author has studied on the influence of the tail tube in an exhaust muffler of cavity-type upon the attenuation characteristics. First, he has found the following results : the longer the tail tube, the more the attenuation effect of exhaust noise increases generally, but this attenuation is not proportional to its length. Moreover, it has been recognized that the diameter of the tail tube brings an important influence on the exhaust noise of the engine, and its effect as an acoustic-filter is determined essentially by the sectional area of the tail tube. Finally, he has obtained better results when the tail tube is divided into small tubes.View full abstractDownload PDF (1533K) -
Tsutomu KANAI1960 Volume 26 Issue 168 Pages 1183-1191
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSTheoretical equations which give attenuation characteristics are presented for many types of mufflers, which are chosen single and multiple chamber mufflers of the expansion chamber, resonators and their modified types, because these mufflers are foundamental components making up practical mufflers and have less flow resistance. Pure sound experiments have been made to investigate attenuation characteristics for these mufflers and to examine applicability of the theories. Results of the pure sound experiments indicate good agreement with these theories. Two disadvantageous characterisitics of the ordinary expansion chamber, which are the periodical pass-frequencies and larger flow resistance than other mufflers, are eliminated by development of an advanced type. The approximate equation, which represents tail pipe effect and is independent of the equations for mufflers themselves, indicates good agreement with the results of the pure sound experiment.View full abstractDownload PDF (1005K) -
Tsutomu KANAI1960 Volume 26 Issue 168 Pages 1191-1196
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSAttenuation characteristics for exhaust noise are influenced by the exhaust gas temperature, flow velocity and non-steady wave. They are investigated theoretically and experimentally by using a specially designed apparatus. Gas temperature has an effect to modify frequency of the attenuation curve without change of attenuated amount, and the effect of flow velocity is negligibly small. Attenuation characteristics for non-steady wave is similar to the one for pure sound, but audible sound inetensity is much larger (about 40 db) than one indicated by instruments. Attenuation characteristics of chambers filled with glass wool are obtained experimentally, and this type shows much efficacy for non-steady wave. Results of the experiments in which mufflers are inserted in the engine exhaust line, agree with those of the theories which are composed of equations on muffler themselves, tail pipe and effects of gas temperature, flow velocity and non-steady wave.View full abstractDownload PDF (778K) -
Seiichi KITANO, Tsutomu KAWAI1960 Volume 26 Issue 168 Pages 1197-1203
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe relation between the increase of vaporization of gas oil and the temperature rise of mixture in the suction pipe has been studied under several conditions of preheating of the fuel oil or intake-air respectively. In the experiment a model horizontal suction pipe and a blower were used. From the results of this and past experiments, it has been ascertained that mixture heating is best, the fuel oil heating is second best and the air heating is worst, to obtain more veporization of fuel oi1 and less temperature rise of mixture in the suction pipe.View full abstractDownload PDF (838K) -
Tomitaro TOYOKURA1960 Volume 26 Issue 168 Pages 1204-1206
Published: August 25, 1960
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSDownload PDF (505K)
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