JP2024030252A - Air compressor performance test system and energy recovery method - Google Patents

Abstract

[Problem] To improve energy efficiency in an air compressor performance testing system. SOLUTION: A performance test system 100 includes an inflow line 10 that is connectable to an outlet 9c of an air compressor 9 and through which compressed air generated by the air compressor 9 flows, and a pressure P1 of the compressed air in the inflow line 10. A pressure regulating valve 14 that adjusts the pressure to the rated pressure of the air compressor 9, a performance measuring device 13 that measures the performance of the air compressor 9 based on the compressed air in the inflow line 10, and a downstream end of the inflow line 10 connected. a pressure storage tank 21 that stores compressed air; an outflow line 20 connected to the pressure storage tank 21; an expander 23 interposed on the outflow line 20 and driven by compressed air from the pressure storage tank 21; 23, and a rotation speed controller 25 that controls the rotation speeds of the expander 23 and the generator 24. [Selection diagram] Figure 1

Description

The present invention relates to an air compressor performance testing system and an energy recovery method in the system.

Patent Document 1 discloses a system for performing a performance test of an air compressor. If the pressure of the compressed air is below a predetermined value, the compressed air is guided to the factory air source line and supplied to the industrial equipment in the factory in order to effectively utilize the compressed air generated by the air compressor during the performance test. be done. If the pressure of the compressed air exceeds a predetermined value, the compressed air is directed to an outlet and released into the atmosphere to protect the industrial equipment.

Japanese Patent Application Publication No. 2005-337081

In the above system, if the compressed air has high energy, it will be released into the atmosphere. Therefore, there is room for improvement in energy recovery efficiency.

An object of the present invention is to improve the efficiency of energy recovery from an air compressor performance testing system.

A first aspect of the present invention has an installation part in which an air compressor is installed, and an upstream end connectable to an outlet of the air compressor installed in the installation part, and the air compressor generates air. a tank inflow line through which compressed air flows; a pressure regulating valve provided on the tank inflow line to adjust the pressure of the compressed air to the rated pressure of the air compressor; a performance measuring device that measures the performance of the air compressor based on compressed air; a pressure accumulator tank that stores the compressed air and has a tank inlet connected to a downstream end of the tank inflow line; a tank outflow line that has an upstream end connected to a tank outlet and through which the compressed air from the pressure accumulator tank flows; and an expansion device that is interposed on the tank outflow line and is driven by the compressed air to expand the compressed air. The present invention provides a performance testing system for an air compressor, including a generator, a generator driven by the expander, and a rotation speed controller that controls the rotation speeds of the expander and the generator.

According to the above configuration, compressed air generated during a performance test of the air compressor is stored in the pressure storage tank, and the expander and eventually the generator are driven by the compressed air stored in the pressure storage tank. Energy can be recovered from high-pressure compressed air, improving energy efficiency in air compressor performance testing systems.

The expander may expand the compressed air and lower its temperature, and the tank outflow line may be connected to an air conditioning outlet.

According to the above configuration, since the air whose temperature has been lowered by the expander is used for air conditioning, it is possible to support energy saving of air conditioning equipment.

An air compressor performance testing system is provided on the tank outflow line between the accumulator tank and the expander, and reduces the pressure of the compressed air depending on the pressure or temperature of the compressed air from the accumulator tank. It may further include a pressure reducing valve.

According to the above configuration, the amount of pressure drop and thus the amount of temperature drop in the expander can be adjusted by the pressure reducing valve, and the temperature of the air discharged from the expander can be adjusted to a temperature suitable for air conditioning.

The expander includes a first expander and a second expander provided downstream of the tank outflow line with respect to the first expander, and the rotation speed controller is configured to control the first expander. The rotation speed of the first expander and the rotation speed of the second expander may be controlled so that the expansion ratios of the second expander are the same.

According to the above configuration, the expander is configured as a two-stage expander, and the expansion ratios of the two expanders are adjusted to be the same, so that energy recovery efficiency is improved.

An air compressor performance testing system is provided on the tank outflow line between the first expander and the second expander, the air compressor being discharged from the first expander and supplied to the second expander. The device may further include a heater that heats the air.

According to the above configuration, since the air whose temperature has been lowered by the first expander is heated and the heated air is supplied to the second expander, the air discharged from the second expander can be adjusted to an appropriate temperature. Additionally, since the amount of electricity recovered by the generator increases, energy recovery efficiency improves.

The air compressor may include a rotor and an actuator that rotationally drives the rotor, and the actuator of the air compressor may operate based on electric power generated by the generator.

According to the above configuration, the power required to execute the performance test is covered by the power regenerated from the compressed air, so that energy saving of the air compressor performance test system is realized.

A plurality of the installation parts and the upstream ends of the tank inflow line are provided, and the plurality of upstream ends are connectable to each of the outlets of the air compressors installed in each of the plurality of installation parts. Good too.

According to the above configuration, in a performance test system capable of simultaneously performing performance tests on a plurality of air compressors, compressed air generated by each air compressor can be stored in a pressure storage tank, and can be effectively used for power generation.

A second aspect of the present invention is to drive the air compressor so that the pressure of compressed air generated by the air compressor becomes a rated pressure, and measure the performance of the air compressor based on the compressed air. storing the compressed air generated by the air compressor in a pressure storage tank; driving an expander with the compressed air from the pressure storage tank; and driving a generator with the expander. , controlling the rotational speed of the expander and the generator, and providing an energy recovery method in an air compressor performance testing system.

According to the present invention, energy efficiency in an air compressor performance testing system is improved.

1 is a conceptual diagram showing a performance test system for an air compressor according to a first embodiment of the present invention. FIG. 3 is a Mollier diagram showing the action of the expander according to the first embodiment. FIG. 2 is a conceptual diagram showing a performance test system for an air compressor according to a second embodiment of the present invention. FIG. 7 is a Mollier diagram showing the action of the expander according to the second embodiment. FIG. 7 is a conceptual diagram showing a performance test system for an air compressor according to a third embodiment of the present invention.

Embodiments of the present invention will be described below with reference to the drawings. Identical or corresponding elements are given the same reference numerals and redundant description will be omitted.

(First embodiment)
Referring to FIG. 1, a performance test system 100 according to the first embodiment is introduced into, for example, a manufacturing factory for air compressors 9, and tests the performance of unshipped air compressors 9 manufactured at the manufacturing factory. test.

The performance test system 100 includes a performance test section 1 and an energy recovery section 2. The performance test section 1 performs a performance test of the air compressor 9 according to a predetermined standard such as an international standard or a Japanese industrial standard. The energy recovery section 2 is added to the performance testing section 1. The energy recovery unit 2 recovers the energy of the compressed air generated by the air compressor 9 during the performance test, converts the recovered energy into other energy such as electric power, and makes it reusable.

The performance testing section 1 includes an installation section 11, a cooler 12, a performance measuring device 13, a pressure regulating valve 14, and a tank inflow line 10. The energy recovery unit 2 includes a pressure storage tank 21 , a pressure regulating valve 22 , an expander 23 , a generator 24 , a rotation speed controller 25 , and a tank outflow line 20 .

The air compressor 9 to be subjected to the performance test is installed in the installation section 11. The tested air compressor 9 is transferred from the installation section 11, and the next air compressor 9 to be tested is transferred to the installation section 11. Hereinafter, the state in which the air compressor 9 is installed in the installation section 11 will be referred to as the "installation state." The type of air compressor 9 is not limited to the axial turbo type, but may be a centrifugal turbo type or a positive displacement type.

Air compressor 9 has a casing 9a, an inlet 9b, an outlet 9c, a rotor 9d, and an actuator 9e. The actuator 9e is, for example, an electric motor. The actuator 9e rotationally drives the rotor 9d. Thereby, the air compressor 9 compresses the air introduced into the casing 9a through the inlet 9b, and discharges the compressed air out of the casing 9a through the outlet 9b.

The upstream end of the tank inflow line 10 can be connected to the outlet 9c of the air compressor 9 in the installed state. The upstream end of the tank inflow line 10 is constructed of, for example, a flexible hose. When the air compressor 9 is transferred to the installation section 11, a worker connects the upstream end of the tank inflow line 10 to the outlet 9c of the air compressor 9. Compressed air generated by the air compressor 9 flows through a tank inlet line 10. After the performance test is completed, a worker removes the upstream end of the tank inflow line 10 from the outlet 9c.

The cooler 12, the performance measuring device 13, and the pressure regulating valve 14 are provided on the tank inflow line 10 in this order when viewed from the air compressor 9. Cooler 12 cools compressed air flowing through tank inlet line 10 . The pressure regulating valve 14 adjusts the pressure P1 of the compressed air so that the pressure P1 of the compressed air generated by the air compressor 9 becomes the rated pressure of the air compressor 9. The rated pressure is the maximum pressure that can guarantee the performance of the air compressor 9 under defined conditions. The performance measuring device 13 measures the performance of the air compressor 9 based on the generated compressed air and in accordance with the standard.

The pressure accumulation tank 21 has a tank inlet 21a and a tank outlet 21b. A downstream end of the tank inflow line 10 is connected to the tank inlet 21a. Compressed air that has passed through the performance measuring device 13 and the pressure regulating valve 14 is supplied to the pressure accumulation tank 21 and stored therein. The pressure of the compressed air decreases in the process of passing through the performance measuring device 13 and the pressure regulating valve 14. The pressure of compressed air in the pressure accumulation tank 21 (hereinafter referred to as tank pressure P21) is lower than the rated pressure.

Tank outlet 21b is connected to the upstream end of tank outflow line 20. The pressure regulating valve 22 and the expander 23 are provided on the tank outflow line 20 in this order when viewed from the pressure accumulation tank 21. The tank outflow line 20 can be divided into an expander supply line 20a from the pressure accumulation tank 21 to the expander 23, and an expander discharge line 20b extending from the expander 23. The expander supply line 20a can be divided into a primary pressure line 20a1 on the upstream side of the pressure regulating valve 22 and a secondary pressure line 20a2 on the downstream side with respect to the pressure regulating valve 22.

The pressure regulating valve 22 reduces the pressure of the compressed air from the pressure storage tank 21 and adjusts the pressure of the compressed air supplied to the expander 23. In this embodiment, the expander 23 is of a displacement type (screw type), but any type of rotary type may be adopted. Expander 23 has an inlet 23a, an outlet 23b, and a rotor 23c. The downstream end of the expander supply line 20a (secondary pressure line 20a2) is connected to the inlet 23a. The upstream end of the expander discharge line 20b is connected to the outlet 23b. The expander 23 expands the compressed air supplied through the inlet 23a and discharges the expanded air through the outlet 23b. The pressure of the air discharged from the expander 23 (hereinafter referred to as expander outlet pressure P23b) is near atmospheric pressure. Further, the expander 23 expands the air and lowers its temperature.

A downstream end of the outflow line 20 (expander discharge line 20b) is connected to an air conditioning outlet 8a. The air outlet 8a is connected to an outdoor unit 8c of an air conditioning facility 8 provided in a manufacturing factory via an air conditioning duct 8b. The air outlet 8a is open to the inside of the manufacturing factory of the air compressor 9, and blows out conditioned air into the manufacturing factory. This allows the temperature inside the manufacturing plant to be adjusted to an appropriate temperature. The expander discharge line 20b is connected to, for example, the air conditioning duct 8b. The air expanded and cooled by the expander 23 is used as air conditioning air.

The rotor 23c of the expander 23 is connected to the rotating shaft 24a of the generator 24. Although FIG. 1 schematically shows that the rotating shaft 24a is directly connected to the rotor 23c, a speed reducer or a speed increaser may be interposed between the expander 23 and the generator 24. When the expander 23 operates, the generator 24 is driven to generate alternating current power.

The rotation speed controller 25 controls the rotation speed of the generator 24 per unit time. Since the generator 24 is mechanically connected to the expander 23, the rotation speed controller 25 controls the rotation speed of the generator 24 by considering the speed ratio of the expander 23 to the generator 24. The rotation speed of the expander 23 can be controlled. The rotation speed controller 25 is realized by, for example, an inverter.

The performance test system 100 includes a controller 3 that controls the operations of the performance test section 1 and the energy recovery section 2, and various sensors 31 to 35 that detect information required for control by the controller 3. The various sensors 31 to 35 include, for example, a test pressure sensor 31, a tank pressure sensor 32, an expander inlet pressure sensor 33, a rotation speed sensor 34, a temperature sensor 35, and the like. The controller 3 controls the operations of the pressure regulating valves 14 and 22 and the rotation speed controller 25, for example.

The test pressure sensor 31 detects the pressure P1 of compressed air 9 generated by the air compressor 9. The test pressure sensor 31 detects the pressure P1 on the upstream side of the performance test section 1 in the tank inflow line 10, for example. Tank pressure sensor 32 detects tank pressure P21. The tank pressure sensor 32 detects the tank pressure P21 within the pressure accumulation tank 21 or in the primary pressure line 20a1, for example. The expander inlet pressure sensor 33 detects the pressure of compressed air supplied to the expander 23 (hereinafter referred to as expander inlet pressure P23a). The expander inlet pressure sensor 33 detects the expander inlet pressure P23a through the secondary pressure line 20a2.

The rotation speed sensor 34 detects the rotation speeds of the generator 24 and the expander 23. The rotation speed sensor 34 may detect the rotation speed of the rotor 23c, the rotation speed of the rotating shaft 24a, or the frequency of alternating current generated by the generator 24. If any one of these is detected, the controller 3 adjusts the rotational speed of both the generator 24 and the expander 23 based on the speed ratio between the expander 23 and the generator 24 and the number of poles of the generator 24. Detectable. The temperature sensor 35 detects the temperature of the air discharged from the expander 23 (hereinafter referred to as expander outlet temperature T23b).

The controller 3 monitors the detection result of the test pressure sensor 31 and controls the pressure regulating valve 14 so that the pressure P1 of the compressed air generated by the air compressor 9 becomes the rated pressure. The controller 3 controls the pressure regulating valve 22 based on the tank pressure P21 and the expander inlet pressure P23a detected by the sensors 32 and 33 so that the expander inlet pressure P23a becomes a predetermined value. The controller 3 monitors the detection result of the rotation speed sensor 34 and performs feedback control of the rotation speed via the rotation speed controller 25 so that the rotation speed is maintained at a predetermined value. In controlling the rotation speed controller 25, the detection result of the temperature sensor 35 may be referred to.

In FIG. 2, the action of the expander 23 is shown using a Mollier diagram in which the horizontal axis represents specific enthalpy (kJ/kg) and the vertical axis represents absolute pressure (MPaA). The thick solid line indicates this embodiment, and the two-dot chain line indicates a reference example. The broken line is an isentropic line, and the total adiabatic efficiency ηad (0.6 as an example) is taken into consideration in both the present embodiment and the reference example. The expander outlet pressure P23b is the same in this embodiment and the reference example. In both the present embodiment and the reference example, the temperature of the compressed air at the inlet 23a of the expander 23 (hereinafter referred to as expander inlet temperature T23a) is the same, and the temperature of the compressed air in the pressure accumulator tank 21 is the same. Almost the same.

In the reference example, compressed air in the pressure storage tank 21 is supplied to the inlet 23a of the expander 23 without being pressure regulated or reduced. In the expander 23, the air pressure decreases from the tank pressure P21 to the expander outlet pressure P23b. At this time, the specific enthalpy decreases from the initial value h21 of the compressed air in the tank 21 to the outlet value h23bref.

Since the pressure drop amount ΔPref in the expander 23 is large (ΔPref=P23a-P23b), the specific enthalpy difference Δhref becomes large (Δhref=h21-h23bref). Although it can be said that the amount of energy recovered increases accordingly, the expander outlet temperature T23bref becomes considerably low.

As just an example, if the rated pressure is 0.8 MPaA, the tank pressure P21 and the expander inlet pressure P23a are 0.7 MPaA, the expander outlet pressure P23b is 0.1 MPaA, and the expander inlet temperature T23a is 40°C, in the reference example, the expander The outlet temperature T23bref is -40.9°C. For this reason, it is difficult to use it as air for air conditioning.

In contrast, in this embodiment, the pressure regulating valve 22 reduces the pressure of the compressed air so that the expander inlet pressure P23a becomes lower than the tank pressure P21. Due to this pressure reduction, the specific enthalpy of the compressed air changes from the initial value h21 to the expander inlet value h23a, but the amount of change is small.

In the expander 23, the air pressure decreases from the expander inlet pressure P23a to the expander outlet pressure P23b. The pressure drop amount ΔP in the expander 23 is smaller than that of the reference example. Therefore, the expander outlet value h23b of specific enthalpy is larger than the reference example, and the specific enthalpy difference Δh is smaller than the reference example. The amount of energy extracted from the compressed air is small, and the expander outlet temperature T23b is higher than the expander outlet temperature T23ref of the reference example.

Just as an example, when the expander inlet pressure P23a is 0.2 MPaA, the expander outlet temperature T23b is 6°C in this embodiment, and when the expander inlet pressure P23a is 0.3 MPaA, in this embodiment, the expander outlet temperature T23b is 6°C. The temperature T23b becomes -11°C. Within this temperature range, the air can be suitably used as air conditioning air, and can help improve the energy efficiency of the air conditioning equipment 8.

The electric power (kW) regenerated from the compressed air in the generator 24 is the product of the specific enthalpy difference Δh and the circulation flow rate (kg/s). In this system 100, the generator 24 operates even when the tank pressure P21 is high. There are more opportunities to recover energy and the energy efficiency of the performance testing system 100 is improved.

Electric power generated by the generator 24 is supplied to the actuator 9e of the installed air compressor 9 via the power supply line 4. Generator 24 functions as at least part of the power source for air compressor 9 in performance test system 100 . The power required to execute the performance test is covered by the power regenerated from the compressed air generated during the performance test, making it possible to save energy in the performance test system 100.

(Second embodiment)
Next, a second embodiment will be described, focusing on differences from the above embodiment.

Referring to FIG. 3, the pressure regulating valve 22 (see FIG. 1) is omitted in the energy recovery unit 2 of the performance test system 100 according to the present embodiment. The expander 23 includes a first expander 23A and a second expander 23B, and is configured in two stages. The second expander 23B is provided downstream of the tank outflow line 20 with respect to the first expander 23A. The downstream end of the expander supply line 20a is connected to the inlet 23Aa of the first expander 23A. The upstream end of the expander discharge line 20b is connected to the outlet 23Bb of the second expander 23B.

An outlet 23Ab of the first expander 23A is connected to an inlet 23Ba of the second expander 23B via an intermediate line 20c. The energy recovery unit 2 further includes a heater 26. The heater 26 is interposed on the intermediate line 20c between the first expander 23A and the second expander 23B, and heats the air discharged from the first expander 23A and supplied to the second expander 23B. .

In this embodiment, the generator 24 includes a first generator 24A driven by a first expander 23A and a second generator 24B driven by a second expander 23B. The first generator 24A and the second generator 24B can be connected to the actuator 9e of the installed air compressor 9 via the power supply line 4. The generator 24 functions as a power source for the air compressor 9 similarly to the first embodiment. Note that one power generator may be driven by the first expander 23A and the second expander 23B.

The rotation speed controller 25 controls the rotation speed of the first generator 24A and the rotation speed of the second generator 24B. To this end, the rotation speed sensor 34 includes a first rotation speed sensor 34A that detects the rotation speed of the first generator 24A, and a second rotation speed sensor 34B that detects the rotation speed of the second generator 24B. The controller 3 refers to the detection results of the two rotational speed sensors 34A and 34B, and makes the expansion ratio of the first expander 23A and the second expander 23B the same, so that the first generator The rotational speeds of the generator 24A and the second generator 24B, as well as the rotational speeds of the first expander 23A and the second expander 23B, are controlled. The expansion ratio is the square root of the value obtained by dividing the expander inlet pressure P23a by the expander outlet pressure P23b. The outlet pressure of the first expander 23A and the inlet pressure of the second expander 23B (hereinafter referred to as intermediate pressure P23c) are the square root of the product of the expander inlet pressure P23a and the expander outlet pressure P23b.

In FIG. 4, similarly to FIG. 2, the operation of the expander 23 according to the present embodiment is shown together with a reference example. The reference example is similar to that shown in FIG.

In this embodiment, the compressed air in the pressure accumulation tank 21 is supplied to the expander 23 without being depressurized as in the reference example. First, the first stage expansion is performed in the first expander 23A, whereby the pressure of the compressed air decreases from the expander inlet pressure P23a, which is equivalent to the tank pressure P21, to the intermediate pressure P23c. As a result, the specific enthalpy decreases from the expander inlet value h23a to the first stage outlet value h23Ab, and the temperature of the air decreases from the expander inlet temperature T23a to the first stage outlet temperature T23Ab.

The air discharged from the first expander 23A is heated by the heater 26 before being supplied to the second expander 23B. As a result, the temperature of the air increases from the first stage outlet temperature T23Ab to the second stage inlet temperature T23Ba. As the temperature rises, the specific enthalpy also increases from the first stage exit value h23Ab to the second stage exit value h23Ba. The second stage inlet temperature T23Ba and the second stage inlet value h23Ba are approximately equal to the expander inlet temperature T23a and the expander inlet value h23a.

After heating the air, a second stage of expansion is performed in the second expander 23B, thereby reducing the pressure of the compressed air from the intermediate pressure P23c to the expander outlet pressure P23b. As a result, the specific enthalpy decreases from the second stage inlet value h23Ba to the expander outlet value T23Bb, and the temperature of the air decreases from the second stage inlet temperature T23Ba to the expander outlet temperature T23b.

The electric power generated in the generator 24 (first generator 24A and second generator 24B) is proportional to the sum of the specific enthalpy difference ΔhA in the first expander 23A and the specific enthalpy difference ΔhB in the second expander 23B. do. The energy increased in the heating process can also be recovered, and the specific enthalpy difference (ΔhA+ΔhB) generated in the entire expander 23 becomes larger than the specific enthalpy difference Δhref of the reference example. Therefore, the amount of power recovered by the generator 24 in this embodiment is larger than that in the comparative example. Therefore, the energy recovery efficiency in the performance test system 100 is further improved.

As just an example, if tank pressure P21 and expander inlet pressure P23a are 0.7 MPaA, expander outlet pressure P23b is 0.1 MPaA, and expander inlet temperature T23a is 40°C, intermediate pressure P23c is 0.26 MPaA, and first stage outlet temperature T23Ab. becomes -6.9℃. When the second stage inlet temperature T23Ba is 40°C, the expander outlet temperature T23b is -5°C. Within this temperature range, the air discharged from the expander 23 can be suitably used as air conditioning air.

(Third embodiment)
Next, a performance test system 100 according to a third embodiment will be described, focusing on changes from the first and second embodiments.

Referring to FIG. 5, even when the expander 23 is of a multi-stage type, a pressure regulating valve 22 may be provided between the pressure accumulating tank 21 and the expander 23.

The compressed air in the pressure storage tank 21 may be used not only for power recovery by the expansion turbo generator but also for other purposes. For example, when processing machines and machine tools installed in the manufacturing equipment of the air compressor 9 are driven by pneumatic pressure, the compressed air in the pressure storage tank 21 may function as a driving source for these pneumatic devices. good.

In this embodiment, as an example, compressed air is used as instrumentation air for a machining machine 59A in a manufacturing facility and as a drive source for a pneumatic impact wrench 59B. The performance test system 100 has equipment lines 50A and 50B that connect the pressure storage tank 21 to these pneumatic equipment 59A and 59B. The pressure accumulation tank 21 has outlet ports 21cA and 21cB in addition to the tank outlet 21b for the expander 23 described above. The upstream ends of the equipment lines 50A, 50B are connected to the outlet ports 23cA, 23cB, respectively, and the downstream ends are connected to the pneumatic equipment 59A, 59B, respectively. Thereby, the compressed air in the pressure storage tank 21 drives the pneumatic equipment in the manufacturing equipment, contributing to energy saving of the entire manufacturing equipment.

In this case, the performance test system 100 may include pressure regulating valves 51A and 51B interposed in the equipment lines 50A and 50B, respectively. The pressure regulating function or pressure reducing function of the pressure regulating valves 51A, 51B makes it possible to supply air at a pressure suitable for each pneumatic device to the pneumatic devices 59A, 59B.

The performance testing section 1 of the performance testing system 100 may include a plurality of installation sections 11. In this case, a plurality of installation parts 11 are provided, and at least the upstream end of the tank inflow line 10 is provided in a plurality so as to correspond to each of the plurality of air compressors 9. In this embodiment, the same number of tank inflow lines 10 as the installation parts 11 are independent from each other. The pressure accumulation tank 21 has a plurality of tank inlets, and the downstream ends of the plurality of tank inflow lines 10 are connected to each of the plurality of tank inlets 21a. However, the tank inflow line 10 may have a single upstream end, and the tank inflow line 10 may be branched/combined between the pressure accumulation tank 21 and the plurality of pressure regulating valves 14.

With this configuration, while the air compressor 9 is being replaced at one installation section 11, a performance test can be conducted at another installation section 11, and compressed air is continuously supplied into the pressure storage tank 21. can be done. Therefore, the energy recovery unit 2 can also be operated continuously, and the operating efficiency of the performance test system 100 is increased.

Although the embodiments of the present invention have been described so far, the above configuration can be changed, added to, and/or deleted as appropriate within the scope of the spirit of the present invention.

For example, if the expander 23 is of a multi-stage type, a single generator may be driven by a plurality of expanders. In this case, a power transmission mechanism is provided that inputs the rotation of the rotors 23c of the plurality of expanders 23 to the rotating shaft 24a of the generator 24. When the expander 23 is of a multistage type, the number of stages is not limited to two.

100 Performance test system 1 Performance test section 2 Energy recovery section 3 Controller 4 Power supply section 8a Air outlet 9 Air compressor 9a Casing 9b Inlet 9c Outlet 9e Actuator 10 Tank inflow line 20 Tank outflow line 21 Pressure accumulation tank 22 Pressure regulating valve (pressure reducing valve) )
23 Expander 23A First expander 23B Second expander 24 Generator 25 Rotation speed controller 26 Heater

Claims (8)

an installation part where the air compressor is installed;
a tank inflow line having an upstream end connectable to an outlet of the air compressor installed in the installation part, through which compressed air generated by the air compressor flows;
a pressure regulating valve that regulates the pressure of the compressed air in the tank inflow line to the rated pressure of the air compressor;
a performance measuring device that measures the performance of the air compressor based on the compressed air in the tank inflow line;
a pressure accumulation tank that stores the compressed air and has a tank inlet connected to the downstream end of the tank inflow line;
a tank outflow line having an upstream end connected to a tank outlet of the pressure accumulation tank, through which the compressed air from the pressure accumulation tank flows;
an expander interposed on the outflow line and driven by the compressed air to expand the compressed air;
a generator driven by the expander;
a rotation speed controller that controls the rotation speeds of the expander and the generator;
Air compressor performance testing system. The expander expands the compressed air and lowers its temperature,
the tank outflow line is connected to an air conditioning outlet;
The air compressor performance testing system according to claim 1. Further comprising a pressure reducing valve that is provided between the pressure accumulation tank and the expander on the tank outflow line and reduces the pressure of the compressed air according to the pressure or temperature of the compressed air from the pressure accumulation tank.
The air compressor performance testing system according to claim 2. The expander includes a first expander and a second expander provided downstream of the tank outflow line with respect to the first expander,
The rotation speed controller controls the rotation speed of the first expander and the rotation speed of the second expander so that the expansion ratios of the first expander and the second expander are the same. ,
The air compressor performance testing system according to claim 1. Further, a heater is provided between the first expander and the second expander on the tank outflow line and heats the air discharged from the first expander and supplied to the second expander. prepare,
The air compressor performance testing system according to claim 4. The air compressor has a rotor and an actuator that rotationally drives the rotor,
the actuator of the air compressor operates based on electric power generated by the generator;
The air compressor performance testing system according to claim 1. A plurality of the installation portions and the upstream end of the tank inflow line are provided,
The plurality of upstream ends are connectable to each of the outlets of the air compressor installed in each of the plurality of installation parts,
The air compressor performance testing system according to claim 1. Operating the air compressor so that the pressure of compressed air generated by the air compressor becomes a rated pressure, and measuring the performance of the air compressor based on the compressed air;
storing the compressed air generated by the air compressor in a pressure storage tank;
Driving an expander with the compressed air from the pressure storage tank, and driving a generator with the expander;
controlling the rotation speeds of the expander and the generator;
An energy recovery method in an air compressor performance testing system comprising: