Hitachi, Ltd.

Hitachi Plant Technologies, Ltd.

Hideo Nishida

Hiromi Kobayashi

Haruo Miura

Kazuki Takahashi

Manabu Yagi

Masanori Tanaka

Tetsuya Kuwano

Takanori Shibata

Naohiko Takahashi

Takashi Eino

Yasuo Fukushima

Sadashi Tanaka

Shinjiro Ueda

Toshio Itou

Kazuo Takeda

Toshio Ito

Takeo Takagi

Tadaharu Kishibe

Yoichi Yoshinaga

Hiroto Yoshikai

Yoshihiro Takada

Junichi Oizumi

Yoshiyuki Nakano

Yozo Hibino

Ichiro Gyobu

Kazuyuki Sugimura

Kazutoshi Yanagihara

Hiroshi Ohmachi

Tomoyuki Ishikawa

Fumio Koseki

A performance prediction device includes: an actual measured data obtaining unit that obtains actual measured data of a compressor; a test gas physical property correction formula database in which test gas physical property correction formulae are stored; a test parameter calculation unit that calculates test parameters of the compressor; and a test parameter correction unit that selects at least one of the test gas physical property correction formulae from the test gas physical property correction formula database based on types and a mix ratio of gases included in a test gas to be used in the prediction and corrects the test parameters by using the selected test gas physical property correction formula.

Performance prediction device and performance prediction method for compressor

An impeller includes a hub plate and a plurality of blades circumferentially disposed at intervals on one surface side of the hub plate. Each blade has a shape formed by piling up a plurality of blade sections in a blade height-wise direction of each blade in a reference impeller in which the hub plate intersects with the blades and which includes a linear element blade in the blade height-wise direction so as to form a curvilinear element blade. In piling up the blade sections, amounts of tangential lean and sweep to be applied to the blade sections are increased as it goes from an end face of at least one of a hub plate side end and a counter hub plate side end toward a span intermediate part of the blade.

Impeller and turbomachinery including the impeller

Turbo machinery comprising an impeller and a diffuser positioned on a downstream side of the impeller that a channel wall surface of the diffuser is composed of a pair of a shroud side diffuser plate and a hub side diffuser plate which surface each other and a channel width is formed so as to be increased downstream, characterized in that guide vanes in a circular arc shape lower in height than the channel width are installed in a line of a plurality of vanes on both channel walls of the shroud side diffuser plate and hub side diffuser plate of the diffuser, and a total of vane heights of the two guide vanes at an outlet of the diffuser is set so as to be within a range from 30 to 70% of the channel width at the outlet of the diffuser.

Turbo machinery

A centrifugal compressor provided with an impeller which is configured to have a plurality of blades arranged at a predetermined interval in a circumferential direction of a hub rotating together with a rotation shaft, in which a blade angle on a shroud side of the blade distributes to have a minimum value at a position between a leading edge of the blade and a midpoint of a camber line on the shroud side, and a maximum value at a position between the midpoint of the camber line on the shroud side and a trailing edge of the blade, and a blade angle of the blade on a hub side distributes so as to have a maximum value at a position between a leading edge and a midpoint of a camber line on the hub side.

Centrifugal compressor

In a high pressure centrifugal compressor, the occurrence of rotating stall noticeable in a comparatively-low specific speed wheel stage is prevented, thereby high efficient fluid performance is obtained and reliability is improved. The centrifugal compressor has a first vaneless diffuser with a constant flow channel height on the downstream side of an impeller, and a second vaneless diffuser in which the flow channel height decreases in a flow direction from an inlet to an outlet on the downstream side of the first vaneless diffuser. These diffusers are combined with an impeller using thick blades.

Centrifugal compressor having vaneless diffuser and vaneless diffuser thereof

A centrifugal compressor is equipped with an impeller having a blade angle distribution that makes it possible to achieve a relatively wide operating range. The blade angle of a shroud side facing a circular plate of a blade is termed a first angle and a blade angle of a hub side disposed at the circular plate is a second. The shroud side is formed in a curved shape having an angle distribution from a front area in a shaft direction toward a centrifugal direction in which the first angle is the local maximum point before a substantially middle portion and the local minimum point after the substantially middle point. The hub side is formed in a curved shape having an angle distribution from the front area in the shaft direction toward the centrifugal direction in which the second angle is the maximum local point before the substantially middle portion.

Centrifugal compressor, impeller and operating method of the same

A multistage centrifugal compressor includes a rotary shaft, and multistage impellers attached to the rotary shaft. Each of the impellers includes a hub, a shroud and blades therebetween in a radial cascade arrangement. An annular suction passage for guiding the fluid flow from the inward radial direction to a blade inlet is disposed upstream of the centrifugal impeller. A diffuser is disposed downstream of the centrifugal impeller. A bend portion is disposed downstream of the diffuser, and a return channel with a guide blade portion is disposed downstream of the bend portion. The annular suction passage at a hub side includes an axial parallel portion.

Multistage centrifugal compressor

In a multistage centrifugal compressor, a plurality of impellers is attached to the same rotary shaft. Vaned Diffusers and vaneless diffusers are used, as diffusers, for respective compressor stages configuring the compressor. The vaned diffusers are continuously used from the first compressor stage to the middle compressor stage, and the vaneless diffusers are used for the last compressor stage and the previous stage. While high efficiency is maintained at the compressor stages having the vaned diffusers, an operating flow range is secured at the compressor stages having the vaneless diffusers.

A turbo compressor, comprising two (2) pieces of rotation shafts, being disposed in parallel with each other, wherein impellers are attached on both ends of one of the rotation shafts, thereby to build up a first-stage compressor and a second-stage compressor, while an impeller on one end of the other rotation shaft, thereby to build up a third-stage compressor. In a lower side of each of the compressors, an intercooler and an after-cooler are disposed in alignment with, for cooling down an operation gas compressed in each stage. The operation gas is guided into the first-stage compressor on a side opposing to a motor, into the second-stage compressor on a side of the motor, and into the third-stage compressor on the side opposing to the motor, in the order thereof.

Turbo compressor

In a fluid machine such as multistage centrifugal compressor, the pressure of a working fluid is raised with the rotation of a impeller. A shaft sealing device is mounted at the end of the rotary shaft in order to prevent the working gas of the raised pressure from leaking out of the fluid machine and then polluting the surroundings. In a case where the fluid machine operates to rotate at high speed, a labyrinth sealing device is employed for the purpose of reducing a frictional loss in the shaft sealing device. The labyrinth sealing device includes a plurality of stages of labyrinth fins which are formed on a casing or the rotary shaft, and a layer of abradable coating to-be-bitten which is formed in the surface part of the rotary shaft or the casing opposing to the labyrinth fins. The clearances between the labyrinth fins and the rotary shaft or the casing are made narrower on the low-pressure side of the labyrinth sealing device than on the high-pressure side thereof. Thus, the fluid machine is run with the minimum clearance. Moreover, even when the coating layer has been lost in touch with the labyrinth fin or by peeling off, the labyrinth fin on the low-pressure side acts as a labyrinth seal.

Labyrinth sealing device, and fluid machine providing the same

In a multi-stage centrifugal compressor, having a plurality of impellers mounted on a rotation shaft, or a single-stage centrifugal compressor, a vaned diffuser, having a plurality of vanes, is mounted at a downstream side of the impeller, and a vaneless diffuser portion is formed downstream of this vaned diffuser. A meridian plane cross-sectional shape of each of two wall surfaces forming the vaneless diffuser portion provided downstream of the vaned diffuser is such that its channel height is decreased progressively in a downstream direction. Instead of this vaneless diffuser, there can be provided a second vaned diffuser having a small number of vanes. In this case, also, two wall surfaces, forming the second vaned diffuser, are contracted progressively in the downstream direction.

Centrifugal compressor and diffuser for centrifugal compressor

A low pressure-side first-stage compressor impeller and a high pressure-side second-stage compressor impeller are mounted respectively on opposite ends of a rotation shaft. A rotor of an electric motor for driving the two impellers is formed at a central portion of the rotation shaft. A stator of the motor is held by a motor casing. The motor casing, a first-stage compressor casing, which cooperates with the first-stage compressor impeller to form a first-stage compressor, and a second-stage compressor casing, which cooperates with the second-stage compressor impeller to form a second-stage compressor, are cast into an integral construction. This integral casing is further formed integrally with an intermediate cooler, disposed downstream of the first-stage compressor, and a discharge cooler disposed downstream of the second-stage compressor. The intermediate cooler and the discharge cooler are disposed below the motor casing in generally parallel relation to the rotation shaft, and the main portions of the two-stage centrifugal compressor are combined into a compact, generally rectangular parallelepiped configuration.

Two-stage centrifugal compressor

A manufacturing method of a rotor for a permanent magnet-excited, high-speed electric rotary machine according to the present invention comprises, covering an outer circumferential surface of at least one permanent magnet by a fiber-reinforced plastic protection cover with prestress compressing in radial direction; inserting a steel sleeve into the at least one permanent magnet to form a permanent magnet assembly; preparing at least one permanent magnet assembly; inserting a rotor shaft into the steel sleeve while applying hydraulic pressure to an inner circumferential surface of the steel sleeve of the prepared at least one permanent magnet assembly to expand the steel sleeve; and then removing the hydraulic pressure to tight fit the at least one permanent magnet assembly onto the rotor shaft.

Rotor for permanent magnet excited, high-speed electric rotary machine,

In a fluid machine such as multistage centrifugal compressor, the pressure of a working fluid is raised with the rotation of a impeller. A shaft sealing device is mounted at the end of the rotary shaft in order to prevent the working gas of the raised pressure from leaking out of the fluid machine and then polluting the surroundings. In a case where the fluid machine operates to rotate at high speed, a labyrinth sealing device is employed for the purpose of reducing a frictional loss in the shaft sealing device. The labyrinth sealing device includes a plurality of stages of labyrinth fins which are formed on a casing or the rotary shaft, and a layer of abradable coating to-be-bitten which is formed in the surface part of the rotary shaft or the casing opposing to the labyrinth fins. The clearances between the labyrinth fins and the rotary shaft or the casing are made narrower on the low-pressure side of the labyrinth sealing device than on the high-pressure side thereof. Thus, the fluid machine is run with the minimum clearance. Moreover, even when the coating layer has been lost in contacting the labyrinth fin or by peeling off, the labyrinth fin on the low-pressure side acts as a labyrinth seal.

Growing community of inventors

Kasumigaura, Japan

Hideo Nishida