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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 22, Issue 113
Displaying 1-14 of 14 articles from this issue
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Itiro TANI1956 Volume 22 Issue 113 Pages 1-2
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSDownload PDF (424K) -
Tokio UEMATU, Keiji HATTA, Hirosi SUGANO1956 Volume 22 Issue 113 Pages 3-6
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSA simplified method is obtained for the calculation of the boundary layer for the retarded flow. The principle of the method is based on the variational method as in the second report, but the expression for the velocity distribution in the boundary layer has been simplified. Also the method of calculation for the accelerated flow is obtained, which is similar to that for the retarded flow. By combining these two methods, it is possible to solve the two-dimensional boundary layer along a cylindrical body of infinite length placed in the uniform flow. As examples, boundary layers around a circular and an elliptic cylinder are calculated and the results are compared with the known experimental values.View full abstractDownload PDF (537K) -
Tokio UEMATU, Keiji HATTA, Sadao NAKAMURA1956 Volume 22 Issue 113 Pages 7-11
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe frictional resistance of a rotating disc in a uniform stream is computed by the variational method. The functionals of the velocity distribution are chosen in such a way that their stationary values give the radial or the peripheral component of the shearing stress on the surface of the disc, and the conditions for the stationary values of the functionals coincide with the equations of motion. We solve these variational problems by Ritz's method, and get the coefficient of the resisting moment cm and the radial component of the shearing stress τr as function of the ratio of the radial to the peripheral velocity. As the results of calculation in the particular cases, we get [numerical formula] for the case of the rotation of the disc alone, and [numerical formula] for the case of the uniform stream alone, where ρ is the density of the fluid, ν the kinematic coefficient of viscosity, ω the angular velocity of the disc, R the radius of the disc, γ the radial distance from the axis of rotation and U the radial component of the potential flow.View full abstractDownload PDF (573K) -
Tosio KAWASAKI, Tadashi SATO1956 Volume 22 Issue 113 Pages 12-18
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSCascade tests were made on a compressor blade with a prescribed pressure distribution. (i) In the tests of cascades of compressor blades, there exists enormous increase in the axial velocity through cascades caused by the growth of boundary layer on both side walls, and the test results deviate considerably from what the two-dimensional potential theory predicts. (ii) In order to estimate the effects of increase in the axial velocity through cascades, a simple two-dimensional model with sources as show in Fig.12 is assumed to represent the actual status, and a calculation is carried out about it. A comparison with experimental results leads to a satisfactory agreement in regard to turning angle and pressure distribution. (iii) The method presented here is considered to afford a correction which deduces two-dimensional characteristics of blades in cascades from data obtained in conventional cascade tunnels, however, further examination with data from various test facilities will be needed.View full abstractDownload PDF (965K) -
Kensaburo TOYODA1956 Volume 22 Issue 113 Pages 19-22
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSNumerous empirical formulas for the discharge coefficient of flow rate over rectangular weirs have been proposed by many authors. Most of them are expressed with utmost fidelity and simplicity based on precise experimental data. The present author deals with the same problem under somewhat simple but logical considerations. The analysis starts from R. von Mises' theoretical investigation of a two-dimensional flow between two parallel walled channel having a slit at the center of the channel end. We assume that the stream lamina in the channel, whether they are horizontal or vertical, contract independently following the Mises' formula. It is natural to consider that near the corners in the weir plane, two directioned contractions experience mutual interference to each other. The author introduces the "interference factor" whose value is determined from an extreme case in which the channel breadth and depth under weir crest are both infinite. Finally the author establishes a generalized formula (8) for the discharge coefficient of rectangular weirs of any proportions, including all possible cases conceivable.View full abstractDownload PDF (583K) -
Tomo-o ISHIHARA, Tomio IDA, Takashi KASAI1956 Volume 22 Issue 113 Pages 23-29
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThis paper deals with first the complete characteristics of P-T-S type normal torque converter including its characteristics under special operating conditions other than the normal power transmitting direction or the range of operating speed ratio, and secodly the effect of air bubble mixed intentionally into the working oil on the characteristics. For experiments, a single-stage normal torque converter with three members was provided. (1) All special operating conditions can be classified into eight cases as given in Table 1. In the vicinity of transition point from a case to the other, discontinuity of characteristics is observed. Excepting this phenomenon, observed characteristics can be deduced qualitatively from the theoretical calculation. (2) So far as she air-content in oil does not exceed a certain limit, the normal characteristics are maintained almost as they are. Increasing the air-content more than the limit, characteristics decrease intensely, particularly in torque, to those of fluid coupling or the like. This limit of content is observed, independently of charging pressure at about 3% decrease of specific weight of air-oil mixture measured at minimum pressure zone in the converter circuit.View full abstractDownload PDF (1354K) -
Hitoshi KINNO1956 Volume 22 Issue 113 Pages 29-33
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSProtection of pump motors against water hammer under the condition of power failure is a very important factor in the design of large pumps and long pipe lines, etc. In this report, the author describes the construction of graphical solution and the method of calculation founded on his new scheme in the case of negligible pipe friction and velocity head. The h-q and m-q diagrams are presented for facilitating the calculation of graphical solution. It is shown that these diagrams are easily derivable from ordinary characteristic curves of pumps. An example of the application of the method is given.View full abstractDownload PDF (677K) -
Hitoshi KINNO1956 Volume 22 Issue 113 Pages 34-39
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSAs a sequel of the preceding paper, this report deals with the system analysis in the scope of normal pump operation. The results obtained are as follows : - (1) The irregularity or pump characteristics has less effect upon estimation or the water hammer phenomenon compared with other elements, such as 2p, K, 2L/a, etc. (2) A convenient chart to estimate the water hammer is presented by use of a couple of h-q and m-q diagrams for wide range pump systems in the scope of practical use. (3) The h-q diagram of pumps will be modified through about 100% by the characteristic of delivery valve, that is the most fredominating element for the water hammer phenomenon over the others.View full abstractDownload PDF (790K) -
Tsuneo ICHIKAWA1956 Volume 22 Issue 113 Pages 40-44
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIn gear pumps which have a relatively small number of gear-teeth, the shifted gears are usually used to avoid the undercutting of the tooth profile. Besides, to equalize the wear of all teeth, the number of teeth of the driving gear is ofen different from that of the driven gear. For such gear pumps the author calculates the ideal delivery, the pulsation of the delivery, the variation or the trapped space, and the relation between the position of the pressure release port and the helical angle.View full abstractDownload PDF (494K) -
Tsuneo ICHIKAWA1956 Volume 22 Issue 113 Pages 44-48
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe author derives theoretically the general equation for the pulsation factor of the delivery pressure of a gear pump and also describes his experiment to record the wave of the pulsating delivery pressure. It is thus found that the number of the delivery pressure pulsation per each revolution is always equal to that of the gear-teeth of the gear, which is coincident with the pulsation of the ideal delivery quantity. If the constructions of the gear pump and the pipe line, the sort of oil, the number of revolutions per unit time and the mean delivery pressure are known, the pulsation factor can be calculated by his theoretical general equation. The values obtained by the experiment are nearly equal to those calculated by the equation.View full abstractDownload PDF (594K) -
Taizo MURAKAMI, Setsuo FUKUNAGA, Masaichi MIYAWAKI, Hiroshi IWAMURO1956 Volume 22 Issue 113 Pages 49-54
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSIt is very difficult to separate the powder particles into two classes, the coarse and the fine, when the particles are fine and have a narrow range of size distribution, as they offer a strong cohesion and agglomomeration property. In order to raise the efficiency of the classifier, it is better to send the fine particles to classifier in a state of mono particles. For this purpose we set a dispersion chamber on this side of the classifier, and in the chamber the powders are blown off with a compressed air jet from a nozzle, striking against a collision plate. Then the powders will be dispersed, and a primary classification of the particles can be effected by the drop of velocity and the sudden change of direction of the air flow. In this study, the classifying characteristic of our classifier having a center core along the center axis of classifying chamber was compared with that of an ordinary type cyclone used as a classifier. As a typical material, we used the powdered particles of MgCO3 having a range of particle size distribution of 1∼23 μ and taking the classifying point at 8 μ.View full abstractDownload PDF (908K) -
Goro KAMIMOTO, Yoshihiro MATSUOKA1956 Volume 22 Issue 113 Pages 55-59
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe 1st report dealed with the fluid dynamical investigations of a model impeller of the centrifugal type hydraulic machinery, which has 4 vanes composed of the logarithmic spiral with the vane angle 30° and inner-outer radii ratio 0.5. In this paper the following model impellers classified into two groups were tested under the measurements of the head, flowing quantities and pressure distributions along the vane surfaces. The one has 4, 6, 8 and 12 vanes composed of logarithmic spiral with the vane angle 30° and inner-outer radii ratio 0.5, and the other has vane angle 30°, 50°, 70° and 90° with 6 vanes and radii ratio of 0.5. Moreover the measurements of the pressure distribution within the passage between the vanes were performed in a few cases in order to investigate the flow within the passage of the impeller.View full abstractDownload PDF (650K) -
Goro KAMIMOTO, Susumu IZUMI, Minoru YAMADA1956 Volume 22 Issue 113 Pages 60-65
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSThe experiments on the guide vanes of the water turbine are often performed under the flow around the vanes without the spiral casing such as the open flume type water turbine. This paper deals with the flow around the guide vanes of the water turbine with the spiral casing and contains the experimental results of the pressure distribution along the vanes and of the circulation flow inside of the guide vanes, cnmposed of 12 pieces of airfoil such as Gottingen 387 or NACA 6512.View full abstractDownload PDF (1170K) -
Goro KAMIMOTO, Nobuhiro IKEGAMI1956 Volume 22 Issue 113 Pages 66-71
Published: January 25, 1956
Released on J-STAGE: March 28, 2008
JOURNAL FREE ACCESSAccording to the experimental results of the autor's 1st report, the characteristics of the guide vanes are suffered closely to the size of the spiral casing and the stalling-phenmena on the vanes occur easily on account of the circulation in the outside of the guide vanes. This paper deals with the flow around the guide vanes of the water turbine with the spiral casings of the various sizes and contains the experimental results of the pressure distribution along the vanes and of the total head losses of the flow through the spiral casing and guide vanes, composed of 12 pieces of airfoil NACA 4512.View full abstractDownload PDF (1047K)
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