CN116710652A

CN116710652A - Fluid mechanical system

Info

Publication number: CN116710652A
Application number: CN202180087575.XA
Authority: CN
Inventors: 西森博信; 斋藤隆史
Original assignee: Hitachi Industrial Equipment Systems Co Ltd
Current assignee: Hitachi Industrial Equipment Systems Co Ltd
Priority date: 2021-01-19
Filing date: 2021-12-20
Publication date: 2023-09-05
Also published as: WO2022158212A1; JP2022112530A; JP7106691B1

Abstract

The present application provides a fluid machine system including a plurality of tank-type fluid machines each having a compressor body for compressing a fluid and a power source for operating the compressor body, the tank-type fluid machines including: a circulation path (150) that connects an exhaust port (109 a) of a first tank-type fluid machine (1 a) with an exhaust port (109 b) of a second tank-type fluid machine (1 b); and a flow path switching device (160) which is located on the path of the circulation path and which allows and restricts the flow of exhaust air discharged to the outside of the circulation path, and which causes at least a part of the exhaust air discharged from the exhaust port of the first tank type fluid machine to flow into the second tank type fluid machine.

Description

Fluid mechanical system

Technical Field

The present application relates to fluid mechanical systems.

Background

Patent document 1 discloses a compressor structure for discharging waste water generated when compressed gas is cooled to the outside without freezing. Patent document 1 describes: "one end of the bypass circuit is made to communicate with the primary side of the aftercooler, and the other end is made to communicate with the waste water circuit that is communicated to the lower end of the waste water collecting portion of the waste water separator. The waste water in the collecting section is discharged as a mixed fluid into the waste water circuit together with a part of the compressed gas in the waste water separator, passes through the throttle section, and then merges with the hot compressed gas introduced through the bypass circuit. Therefore, the compressed gas in the above-described mixed fluid is not drastically reduced in pressure due to the subsequent atmospheric discharge, and as a result, exhaust noise is reduced and freezing of wastewater is prevented.

Prior art literature

Patent literature

Patent document 1: japanese patent laid-open No. 2003-176784

Disclosure of Invention

Technical problem to be solved by the application

As described in patent document 1, there are portions in the internal structure of a fluid machine such as a compressor that are not allowed to freeze. In the installation environment of the fluid machine, the outside air temperature of the installation environment is an important condition, and for example, when the outside air temperature is below the freezing point, there is a concern that the circulating water and the lubricating oil freeze and viscosity increase, and the electronic equipment freeze, and the like. When installed in a low-temperature environment, techniques for efficiently protecting against freezing and the like are required.

Means for solving the technical problems

In order to solve the above-described problems, the present application discloses various techniques for solving the above-described problems, and as an example, provides a fluid machine system having a plurality of box-type (package-type) fluid machines each having a compressor main body that compresses a fluid and a power source that operates the compressor main body, the fluid machine system including: a circulation path that connects an exhaust port of the first tank-type fluid machine with an exhaust port of the second tank-type fluid machine; and a flow path switching device which is located on the path of the circulation path, and which allows and restricts the flow of exhaust air discharged to the outside of the circulation path, and which causes at least a part of the exhaust air discharged from the exhaust port of the first tank type fluid machine to flow into the second tank type fluid machine.

Technical effects

According to the present application, in a fluid machine system installed in a place where the outside air temperature is low, such as an environment below the freezing point, for example, the heat of the exhaust air fluid machine having a relatively high discharge temperature can be used to prevent freezing of other fluid machines that are stopped or have a low load.

The problems, structures, and effects other than those described above will be apparent from the following description of the embodiments.

Drawings

Fig. 1 is a schematic view showing the structure of a box compressor system according to an embodiment of the present application.

Fig. 2 is a schematic diagram showing a state when exhaust air from one of the box compressors flows into the other box compressor in the box compressor system shown in fig. 1.

Fig. 3 is a schematic view showing a state when the discharge air of one of the box compressors and the discharge air of the other box compressor are discharged to the outside of the external duct in the box compressor system shown in fig. 1.

Detailed Description

Hereinafter, modes for carrying out the present application will be described with reference to the drawings.

Fig. 1 shows a schematic configuration of a compressor system according to the present embodiment. The compressor system includes a plurality of first box compressors 1a and second box compressors 1b, and is configured such that cooling air flowing through the inside thereof is connected via an external duct 150. The following description will be given of the configuration, and in this embodiment, the first and second box compressors 1a and 1b use the same compressor, and the description will be mainly given for the first box compressor 1 a.

In the first box compressor 1a, components such as the drive source 101a, the speed increaser 102a, the primary compressor body 103a, and the secondary compressor body 104a are mounted on a common base (not shown), and the side surfaces (four side surfaces in the present embodiment) and the top surface have a cover 105a covering the entire components.

The driving source 101a is a motor. The drive source 101a supplies a rotational force as a driving force to the primary compressor body 103a and the secondary compressor body 104a via the speed increaser 102 a. In this embodiment, the motor is used as a driving source, and an internal combustion engine or a driving source using natural energy such as wind power or water power can be used as another driving source. The case where the driving source 101a has a self-excited fan for introducing air from the outside of the cover 105a into the inside is described, but the external air may be introduced by using a separate excited fan.

The speed increaser 102a is constituted by a combination of a pinion (pin gear) and a bull gear (bull gear), for example, and is mechanically connected to the primary compressor body 103a, the secondary compressor body 104a, and the drive source 101 a. The speed increaser 102a transmits the rotational force from the driving source 101a to the primary compressor body 103a and the secondary compressor body 104a, and changes the rotational speed ratio of the primary compressor body 103a and the secondary compressor body 104 a. The speed increaser 102a is not limited to this, and may be a power transmission mechanism using a chain, a belt, a pulley, or the like. In the present embodiment, the speed increaser 102a is included, but a direct connection structure in which the compressor main body and the driving source are not used may be applied.

The first-stage compressor body 103a and the second-stage compressor body 104a each have a volumetric compression mechanism, for example, and constitute a two-stage compressor. As the positive displacement compressor, various types such as screw type, scroll type, reciprocating type, claw type, and the like can be applied. The present embodiment is not limited thereto. For example, the present embodiment can also be applied to a multistage structure having a compressor body in addition to the primary compressor body 103a and the secondary compressor body 104 a. Alternatively, the primary compressor body 103a and the secondary compressor body 104a may function as a single-stage compressor body.

The cover 105a has an air inlet 107a and an air outlet 109a on the side or top surface, which communicate with the outside. The intake port 107a is connected to an internal intake duct 106a that introduces outside air from the opposite side of the driving source 101a, i.e., the output side of the motor, to the inside of the cover 105a. By the rotation of the self-excited fan of the driving source 101a, the outside air is introduced into the first box compressor 1 a. Some of the outside air introduced from the air inlet 107a is used as cooling air for the components such as the drive source 101a, the speed increaser 102a, the primary compressor body 103a, and the secondary compressor body 104a, and some is sucked into the primary compressor body 103a. In the case of having an air-cooled heat exchanger for cooling the compressed gas, the outside air may be used for the heat exchange.

In the present embodiment, the intake port 107a is disposed on the downstream side of the drive source 101a, and the exhaust port 109a is disposed on the compressor bodies (103 a and 104 a) side. That is, the compressor generally has a tendency to be a higher-temperature heat generating body for the primary compressor body 103a and the secondary compressor body 104a than for the heat generation of the drive source 101a due to the compression heat. Therefore, the respective structural members are cooled with the outside air in order of relatively low temperature.

The exhaust port 109a is connected to an internal exhaust duct 108a extending into the casing 105a, and external air introduced into the inside of the box compressor 1a (excluding external air sucked into the compressor body) is discharged to the outside of the box compressor 1a (an external duct 150 described later).

The control unit 110a is a device that performs various controls of the first box compressor 1a, and is a control device (may be partially or entirely of an analog structure) realized by cooperation of an arithmetic device and a program, for example. The power conversion device 111a changes the ON/OFF (ON/OFF) and the power frequency of the power supplied to the motor, which is the driving source 101a, in accordance with the instruction of the control unit 110a, thereby operating the first box compressor 1a at a variable speed. The shift operation includes, for example, a P control operation, a PI control operation, a PID control operation, a load/no-load operation, or the like. The control unit 110a may be configured as an external control device connected via a wired or wireless communication line.

Next, the external conduit 150 and the flow path switching device 160 will be described. The outer conduit 150 functions as a circulation path connecting the discharge port 109a of the first tank compressor 1a and the discharge port 109b of the second tank compressor 1 b. The flow path switching device 160 is located in the middle flow path of the outer pipe 150, and is a flow path switching mechanism that allows or restricts the discharge air flowing in the outer pipe 150 to be discharged outside the outer pipe 150. In the present embodiment, a rotatable plate which can be tilted by rotation is used, but the present application is not limited to this configuration. The outer pipe 150 can be manually or automatically switched in rotation, and the rotation angle thereof (i.e., the opening degree of the discharge wind flowing in the outer pipe to the outside discharge of the outer pipe) can also be switched in multiple stages.

Fig. 2 shows an outline of the operation of the present embodiment. First, during operation (for example, during full-speed operation), the first box compressor 1a cools the internal heat generating body and then discharges high-temperature exhaust air (cooling air) from the exhaust port 109a to the external conduit 150. At this time, when the second box compressor 1b is stopped or is in no-load operation, if the outside air temperature is equal to or lower than a predetermined temperature, the temperature of the components such as the motor, the primary compressor body 103b, and the secondary compressor body 104b, which are the driving source 101b included in the second box compressor 1b, is relatively low. This low-temperature state may cause freezing of the components of the second box compressor 1b, increase in viscosity of the lubricating fluid (oil or water), and cause load or failure in starting or switching to the load operation.

In view of this, one of the features of the present embodiment is to heat the exhaust air of the first tank compressor 1a having a relatively high heat generation amount by the operation by flowing the exhaust air into the second tank compressor 1b having a relatively low heat generation amount through the external duct 150, thereby suppressing freezing which may become an obstacle when the second tank compressor 1b is started up and switched to the load operation, or an increase in viscosity of the lubricating fluid.

More specifically, by making the flow path switching device 160 "closed (prohibiting or restricting discharge from the external conduit to the outside)", part or all of the high-temperature discharge air from the first casing compressor 1a flows from the discharge port 109b of the second casing compressor 1b to the second casing compressor 1b, and the components of the second casing compressor 1b are heated.

Next, a case where the second box compressor 1b is also started or shifted to the load operation will be described.

Fig. 3 is a diagram showing the flow of cooling air when the flow path switching device 160 is "on (fully on)". In this case, the high-temperature cooling air flowing out from each of the exhaust port 109a of the first box compressor 1a and the exhaust port 109b of the second box compressor 1b is discharged in the direction indicated by the arrow to the outside of the external duct 150 by the flow path switching device 160, and a normal cooling effect can be expected.

As described above, according to the present embodiment, the second box compressor 1b that is in a stopped state or in a low load state can be heated simply by the high-temperature exhaust air of the other first box compressor 1a having a relatively large amount of heat generation, and equipment maintenance and degradation of the performance can be suppressed simply in accordance with the outside air temperature. In particular, in the case type compressor requiring heating, exhaust heat can be utilized without adding a special heating mechanism or energy, and therefore, the energy saving effect is also facilitated.

The embodiments of the present application have been described above, but the present application is not limited to the above-described various configurations, and various modifications can be made without departing from the gist thereof. For example, the box compressors are not limited to 2, but may be composed of 3 or more, and the types and rated specifications of the compressor bodies used in the respective box compressors may be different. For example, when one of the rated specifications is larger than the other, the opening degree of the flow path switching device 160 may be appropriately adjusted so that excessive heating is not performed.

In the case of a system that generates compressed gas by so-called a plurality of numerical control in which a plurality of box compressors and a plurality of discharge pipe systems are combined, the opening degree of the flow path switching device 160 can be automatically adjusted according to switching between the operation and the stop of each box compressor.

In the present embodiment, the compressor body that generates the compressed gas from the atmosphere (air) is described, but the compressor body may be a fluid machine that compresses other gases.

Description of the reference numerals

1a … … first box compressor, 1b … … second box compressor, 101a … … first box compressor drive source, 101b … … second box compressor drive source, 102a … … first box compressor speed increaser, 102b … … second box compressor speed increaser, 103a … … first box compressor primary compressor body, 103b … … second box compressor primary compressor body, 104a … … first box compressor secondary compressor body, 104b … … second box compressor secondary compressor body, 105a … … first box compressor hood, 105b … … second box compressor hood, 106a … … first box compressor internal air intake duct, 106b … … second-case compressor internal intake duct, 107a … … first-case compressor intake port, 107b … … second-case compressor intake port, 108a … … first-case compressor internal exhaust duct, 108b … … second-case compressor internal exhaust duct, 109a … … first-case compressor exhaust port, 109b … … second-case compressor exhaust port, 110a … … first-case compressor control section, 110b … … second-case compressor control section, 111a … … first-case compressor power conversion device, 111b … … second-case compressor power conversion device, 150 … … external duct, 160 … … flow path switching device.

Claims

1. A fluid machine system having a plurality of box-type fluid machines having a compressor body that compresses a fluid, and a power source that operates the compressor body, the fluid machine system comprising:

a circulation path that connects an exhaust port of the first tank-type fluid machine with an exhaust port of the second tank-type fluid machine; and

a flow path switching device which is positioned on the path of the circulation path and allows and restricts the flow of exhaust air discharged to the outside of the circulation path,

at least a portion of exhaust air discharged from an exhaust port of the first tank-type fluid machine flows into the second tank-type fluid machine.

2. The fluid machine system according to claim 1, wherein:

the first tank-type fluid machine is in operation, and the second tank-type fluid machine is stopped or has a lower load than the first tank-type fluid machine.

3. The fluid machine system according to claim 1, wherein:

the flow path switching device allows the flow of exhaust air discharged to the outside of the circulation path when the second tank-type fluid machine is switched from the stop operation to the load operation or from the no-load operation to the load operation.

4. The fluid machine system according to claim 1, wherein:

at least 1 of the tank-type fluid machines has a rated specification different from that of the other tank-type fluid machines.

5. The fluid machine system according to claim 1, wherein:

the tank-type fluid machine is a tank-type compressor, and generates compressed gas from the atmosphere.