JP2022185735A - Operation control method for engine driven compressor and engine driven compressor - Google Patents

Abstract

To prevent shortage in fuel supply to a compressor body immediately after being shifted from a warm-up operation state with start-up load reduced to a normal operation state.SOLUTION: An engine driven compressor 1 has a pressure control valve 13 which opens and closes a control flow passage 12 communicating a valve closing pressure receiving chamber of an intake control valve 11 controlling intake air of a compressor body 40 with a receiver tank 60. The pressure control valve 13 performs opening and closing control of the intake control valve 11 so as to make pressure inside the receiver tank 60 close to predetermined rated pressure. When warm-up operation is started, control over the intake control valve 11 with the pressure control valve 13 is deactivated and the intake control valve 11 is closed along with a start-up of an engine. Before a warm-up operation stopping condition is met after the start-up, pressure inside the receiver tank 60 is increased to fuel supply start pressure which is less than the rated pressure with the intake control valve 11 opened to a predetermined opening less than a full opening. Then, the warm-up operation is completed and shifted to normal operation in which the intake control valve 11 is controlled with the pressure control valve 13.SELECTED DRAWING: Figure 1

Description

TECHNICAL FIELD The present invention relates to an operation control method for an engine-driven compressor, and an engine-driven compressor for executing the operation control method. The present invention relates to an operation control method for an engine-driven compressor and an engine-driven compressor that executes the operation control method.

Engine-driven compressors equipped with engines such as diesel engines as a drive source for driving the compressor body are widely used for outdoor work such as civil engineering work sites and construction sites where it is difficult to secure a power source.

As such an engine-driven compressor, FIG. 9 shows an example configuration of an engine-driven compressor 300 equipped with an oil-cooled compressor body 340 that compresses the gas to be compressed together with lubricating oil and discharges it as a gas-liquid mixed fluid. shown in

The engine-driven compressor 300 is provided with a receiver tank 360 for separating lubricating oil discharged from the compressor body 340 together with the compressed gas, in addition to the compressor body 340 and the engine 350 described above. The compressed gas from which the lubricating oil has been separated in the receiver tank 360 is further removed of the oil via the oil separator 366, and then supplied to the consumption side to which an air working machine (not shown) is connected. is configured to

The lubricating oil collected in the receiver tank 360 can be supplied to the compressor main body 340 through an oil supply passage 364 having an oil cooler 363 and an oil filter 367 using the pressure in the receiver tank 360. configured to allow

In such an engine-driven compressor 300, in order to be able to supply compressed gas at a stable pressure to the consumer side, the compressor body 340 is controlled according to the pressure in the receiver tank 360. An intake adjusting device 310 is provided to adjust the amount of intake air.

As the intake air regulating device 310, the engine-driven compressor 300 shown in FIG. is provided.

The unloader regulator 316 is communicated with the receiver tank 360 via the control channel 312, and the control channel 312 has a pressure regulator that opens the control channel 312 when the pressure in the receiver tank 360 is equal to or higher than a predetermined rated pressure. A valve 313 is provided.

9 is a release passage, and when the pressure regulating valve 313 closes the control passage 312 and the introduction of the compressed gas to the unloader regulator 316 is stopped, the compressed gas in the pressure receiving chamber of the unloader regulator 316 is released. Air is released through the throttle 315, and the unloader regulator 316 can be returned to the fully open position by the biasing force of a return spring (not shown).

By providing the intake air regulating device 310 configured in this way, when the pressure in the receiver tank 360 becomes equal to or higher than the rated pressure, the pressure regulating valve 313 starts the valve opening operation and the unloader regulator 316 controls the compression of the receiver tank 360. When the introduction of gas is started, the intake regulating valve 311 throttles or closes the intake port 341 of the compressor body 340, and when the pressure in the receiver tank 360 drops below the rated pressure, the pressure regulating valve 313 closes and intake air By opening the intake port 341 of the compressor body 340 with the adjustment valve 311, the intake air of the compressor body 340 is adjusted so that the pressure in the receiver tank 360 approaches the above-described rated pressure.

In the engine-driven compressor 300 configured as described above, the engine 350, which is the driving source of the compressor body 340, has a small torque in a low rotation range, and is likely to stall if a load is applied at the time of starting.

In particular, due to the demand for downsizing engines to comply with exhaust gas regulations, engine-driven compressors equipped with small engines with increased maximum output by adopting a common rail system or adding a turbocharger. , the starting torque of the engine is smaller than that of a conventional engine that produces a similar maximum output, and stalling at start-up is more likely to occur.

On the other hand, in the engine-driven compressor 300, the compressor body 340, which is the load on the engine 350, is directly connected to the engine 350, and the engine 350 receives the load associated with the rotation of the compressor body 340 from the start of the engine. Therefore, if the load received from the compressor body 340 can be reduced as much as possible when starting the engine 350, the engine 350 can be started smoothly.

Focusing on the configuration of such an engine-driven compressor 300, in order to reduce the load applied to the engine 350 at the time of starting, Patent Document 1 described later discloses a starting load reducing device indicated by reference numeral 320 in FIG. is disclosed.

The starting load reduction device 320 is composed of a bypass flow path 321 that bypasses the pressure regulating valve 313 and communicates between the unloader regulator 316 and the receiver tank 360, and a bypass valve 325 that opens and closes the bypass flow path 321. By operating the bypass valve 325 to open the bypass flow path 321 at the time of start-up, the unloader regulator 316 can be directly communicated with the receiver tank 360 without passing through the pressure regulating valve 313 .

As a result, when the engine 350 is started with the bypass flow path 321 opened in this way, the compressor body 340 starts rotating and the pressure in the receiver tank 360 rises, the unloader regulator 316 operates to adjust the intake air. By closing the valve 311 and putting the compressor main body 340 into no-load operation, the load on the engine 350 at the start of the start can be reduced.

After the operating state of the engine 350 is stabilized, the bypass valve 325 provided in the starting load reduction device 320 is operated to close the bypass flow path 321, and the pressure regulating valve 313 is controlled according to the pressure in the receiver tank 360. By shifting to normal operation in which the passage 312 is opened and closed, it is configured to be able to perform a known intake adjustment.

In addition, the above-mentioned Patent Document 1 discloses a configuration in which a manual on-off valve is provided as the bypass valve 325, but by changing this to a solenoid valve, it is possible to change the detected operating state of the engine. Based on this, an engine-driven compressor has also been proposed in which the opening/closing operation of the bypass valve 325 can be electrically controlled (see Patent Document 2).

JP-A-2002-168177 JP 2017-115598 A

As described above, in a configuration in which the bypass valve 325 is configured by a solenoid valve and whose opening and closing can be electrically controlled, the engine is started with the bypass valve 325 open, as shown in FIG. By doing so, as soon as the compressor body starts rotating together with the engine, the intake adjustment valve 311 is closed immediately, and warm-up is performed in a state where the starting load is reduced. As shown in FIG. 10B, the bypass valve 325 is closed so that the pressure regulating valve 313 can switch to normal operation in which the control flow path 312 is opened and closed according to the pressure in the receiver tank 360. .

In this way, the engine can be started in a state where it is difficult to stop (stall) by starting the engine and performing the warm-up operation while the load is reduced as much as possible.

However, in the engine-driven compressor configured in this way, as shown in FIG. is in a low pressure state of 0.1 MPa in gauge pressure as an example [see FIG. 11(B)].

Therefore, since the pressure regulating valve 313 is in a closed state, the bypass valve 325 is closed to terminate the warm-up operation and shift to normal operation. The valve 311 opens (Fig. 10(B)), the compressor main body 340 starts compression, and the pressure in the receiver tank 360 rises to a pressure higher than the rated pressure (see Fig. 11(B)).

Due to this pressure increase in the receiver tank 360, the amount of oil supplied to the compressor main body 340 increases, but the increase in the amount of oil supplied to the compressor main body 340 occurs after the pressure inside the receiver tank 360 rises. Therefore, during the period from the shift to normal operation until the pressure in the receiver tank 360 rises to some extent, the gas to be compressed is compressed in a state in which a sufficient amount of lubricating oil is not supplied.

Due to the lack of oil supply, the compression heat generated in the compressor body 340 is not sufficiently cooled, and the discharge temperature of the compressor body 340 rises excessively, resulting in the generation of particularly high-pressure compressed gas. In the compressor main body 340, an abnormal rise in the discharge temperature causes malfunctions such as an emergency stop of the engine-driven compressor.

Therefore, the present invention was made in order to eliminate the drawbacks of the above-mentioned prior art. An operation control method for an engine-driven compressor capable of resolving insufficient lubrication to the main body of the compressor and, as a result, preventing abnormal rise in discharge temperature due to insufficient lubrication, and the operation control method. The object is to provide an engine driven compressor that performs.

Means for solving the problems are described below together with the symbols used in the mode for carrying out the invention. This code is for clarifying the correspondence between the description of the claims and the description of the mode for carrying out the invention, and needless to say, it is used restrictively to interpret the technical scope of the present invention. It is not something that can be done.

In order to achieve the above object, the operation control method for an engine-driven compressor of the present invention comprises:
An engine (not shown), an oil-cooled compressor body 40 driven by the engine, and a gas-liquid mixed fluid of compressed gas and lubricating oil discharged from the compressor body 40 is introduced into the compressed gas and the lubricating oil. a receiver tank 60 for supplying the separated lubricating oil to the compressor body 40 using internal pressure, an intake adjustment valve 11 for controlling the intake air to the compressor body 40, The control flow path 12 communicating between the closing valve pressure receiving chamber 113 and the receiver tank 60, and the control flow path 12 is opened when the pressure in the receiver tank 60 is equal to or higher than a predetermined rated pressure, and the control flow path 12 is opened when the pressure is less than the rated pressure. In the operation control method of the engine-driven compressor 1 having the pressure control valve 13 for controlling the opening/closing operation of the intake control valve 11 by closing the control flow path 12,
Invalidating the control of the intake regulating valve 11 by the pressure regulating valve 13, closing the intake regulating valve 11 when the engine is started, and starting warm-up,
After the engine is started and before a predetermined warm-up termination condition is satisfied, the intake control valve 11 is opened to a predetermined degree of opening less than full opening, thereby reducing the pressure in the receiver tank 60 to the rated pressure. Perform discharge pressure increase processing to increase the lubrication start pressure, which is a predetermined low pressure,
When the warm-up end condition is satisfied, the warm-up operation is ended and the pressure control valve 13 controls the intake control valve 11 to shift to normal operation (claim 1). .

A bypass flow path 20 (21, 22) is provided to bypass the pressure regulating valve 13 and communicate between the receiver tank 60 and the closed valve pressure receiving chamber 113 of the intake regulating valve 11, and the bypass flow path 20 (21, 22), the intake control valve 11 is controlled by the pressure control valve 13 by starting the engine in a state where the receiver tank 60 and the valve closing pressure receiving chamber 113 of the intake control valve 11 are in communication. Disabling, closing the intake control valve 11 at the same time as starting the engine,
The discharge pressure increasing process is performed by throttling the flow rate of the compressed gas introduced into the valve closing pressure receiving chamber 113 of the intake control valve 11 through the bypass passage 20 (21, 22),
By closing the bypass flow path 20 (21, 22), the warm-up operation may be terminated and the pressure control valve 13 may control the intake control valve 11 to shift to normal operation. (Claim 2).

or
a starting control flow path 51 that bypasses the pressure regulating valve 13 and communicates between the closed valve pressure receiving chamber 113 of the intake regulating valve 11 and the receiver tank 60;
When the pressure in the receiver tank 60 is a predetermined high pressure with respect to the oil supply start pressure and is equal to or higher than the starting unload pressure, which is a predetermined low pressure with respect to the rated pressure, the start control flow path 51 is opened. a starting pressure regulating valve 52 that opens and closes the starting control flow path 51 when the starting unload pressure is less than the starting unload pressure, thereby controlling the opening/closing operation of the intake regulating valve 11;
After the discharge pressure increasing process, before the warm-up end condition is satisfied, the intake control valve 11 is controlled by the starting pressure control valve 52,
When the warm-up end condition is satisfied, the control of the intake regulating valve 11 by the starting pressure regulating valve 52 is ended and the warm-up operation is ended. (Claim 3).

Even in the configuration in which the starting control flow path 51 and the starting pressure regulating valve 52 are provided, the pressure regulating valve 13 is bypassed and the receiver tank 60 and the valve closing pressure receiving chamber 113 of the intake regulating valve 11 are communicated with each other. A bypass passage 20 (21, 22) is provided, and the engine is operated in a state in which the receiver tank 60 and the valve closing pressure receiving chamber 113 of the intake control valve 11 are communicated through the bypass passage 20 (21, 22). By starting the, the control of the intake regulating valve 11 by the pressure regulating valve 13 and the starting pressure regulating valve 52 is invalidated, and the intake regulating valve 11 is closed at the same time as the engine is started,
The discharge pressure increasing process is performed by throttling the flow rate of the compressed gas introduced into the valve closing pressure receiving chamber 113 of the intake control valve 11 through the bypass passage 20 (21, 22),
After a predetermined time has passed since the discharge pressure increasing process, the bypass flow path 20 (21, 22) may be closed and the control of the intake regulating valve 11 by the starting pressure regulating valve 52 may be started. Good (claim 4).

In any of the above configurations, the discharge pressure increasing process may be performed while increasing the degree of opening of the intake control valve 11 stepwise (claim 5).

Further, in the configuration in which the starting control flow path 51 and the starting pressure regulating valve 52 are provided, a plurality of the starting control flow paths 51 (51a, 51b . . . 51z) are provided, 51z) are provided with the starting pressure regulating valves 52 (52a, 52b, . ，
After the discharge pressure increasing process, the control of the intake regulating valve 11 by the starting pressure regulating valve 52 (52a, 52b . The pressure control valves 52 (52a, 52b, . . . 52z) may be switched from the one with the lowest operating pressure to the one with the highest operating pressure at predetermined time intervals (Claim 6).

Further, the engine-driven compressor 1 of the present invention is
An engine (not shown), an oil-cooled compressor body 40 driven by the engine, and a gas-liquid mixed fluid of compressed gas and lubricating oil discharged from the compressor body 40 is introduced into the compressed gas and the lubricating oil. a receiver tank 60 for supplying the separated lubricating oil to the compressor body 40 using internal pressure, an intake adjustment valve 11 for controlling the intake air to the compressor body 40, The control flow path 12 communicating between the closing valve pressure receiving chamber 113 and the receiver tank 60, and the control flow path 12 is opened when the pressure in the receiver tank 60 is equal to or higher than a predetermined rated pressure, and the control flow path 12 is opened when the pressure is less than the rated pressure. In the engine-driven compressor 1 equipped with a pressure regulating valve 13 that controls the opening/closing operation of the intake regulating valve 11 by closing the control passage 12,
a bypass passage 20 that bypasses the pressure regulating valve 13 and communicates between the receiver tank 60 and the closed valve pressure receiving chamber 113 of the intake regulating valve 11;
a channel area changing device (23, 24) for making the channel area of the bypass channel 20 variable;
A control device (controller) 30 for controlling the flow path area changing device (23, 24) is provided,
By the control device (controller) 30 controlling the flow path area changing device (23, 24),
When the engine is started, the passage area of the bypass passage 20 is maximized, so that the intake control valve 11 is closed at the same time as the engine is started, and warm-up operation is started;
After the engine is started and before a predetermined warm-up end condition is satisfied, the flow area of the bypass flow path 20 is reduced to open the intake control valve 11 to a predetermined opening degree less than full opening, In addition to performing a discharge pressure increase process for increasing the pressure in the receiver tank 60 to the refueling start pressure, which is a predetermined lower pressure than the rated pressure,
When the warm-up end condition is satisfied, the bypass flow path 20 is closed to end the warm-up operation, and the pressure control valve 13 controls the intake control valve 11 to shift to normal operation. (Claim 7).

Further, another engine-driven compressor 1 of the present invention is
An engine (not shown), an oil-cooled compressor body 40 driven by the engine, and a gas-liquid mixed fluid of compressed gas and lubricating oil discharged from the compressor body 40 is introduced into the compressed gas and the lubricating oil. a receiver tank 60 for supplying the separated lubricating oil to the compressor body 40 using internal pressure, an intake adjustment valve 11 for controlling the intake air to the compressor body 40, The control flow path 12 communicating between the closing valve pressure receiving chamber 113 and the receiver tank 60, and the control flow path 12 is opened when the pressure in the receiver tank 60 is equal to or higher than a predetermined rated pressure, and the control flow path 12 is opened when the pressure is less than the rated pressure. In the engine-driven compressor 1 equipped with a pressure regulating valve 13 that controls the opening/closing operation of the intake regulating valve 11 by closing the control passage 12,
a bypass flow path 20 and a start control flow path 51 that bypass the pressure regulating valve 13 and communicate between the receiver tank 60 and the closed valve pressure receiving chamber 113 of the intake regulating valve 11;
a channel area changing device (23, 24) for making the channel area of the bypass channel 20 variable;
The starting control flow that opens when the pressure on the discharge side of the compressor body 40 is equal to or higher than the starting unload pressure, which is a predetermined low pressure relative to the rated pressure, and closes when the pressure is less than the starting unload pressure. a starting pressure regulating valve 52 provided in the passage 51;
a starting control flow path electromagnetic valve 53 provided in the starting control flow path 51 and communicating in series with the starting pressure regulating valve 52;
A control device (controller) 30 for controlling the flow path area changing device (23, 24) and the start control flow path solenoid valve 53 is provided,
The control device (controller) 30 is
When the engine is started, the solenoid valve 53 for the start control flow path is opened, and the flow area changing device (23, 24) is operated to maximize the flow area of the bypass flow path 20. When the engine is started, the intake control valve 11 is closed to start warm-up,
After the engine is started and before a predetermined warm-up end condition is satisfied, the passage area changing device (23, 24) is controlled to reduce the passage area of the bypass passage 20 to adjust the intake air. By opening the valve 11 to a predetermined degree of opening less than full opening, a discharge pressure increase process is performed to increase the pressure in the receiver tank 60 to the refueling start pressure, which is a predetermined lower pressure than the starting unload pressure,
After the discharge pressure increasing process, the bypass flow path 20 is closed before the warm-up end condition is satisfied, and the control of the intake control valve 11 by the starting pressure control valve 52 is started,
When the warm-up end condition is satisfied, the starting control flow solenoid valve 53 is closed to end the control of the intake control valve 11 by the starting pressure control valve 52, and the warm-up is ended. It is characterized by shifting to normal operation in which the intake control valve 11 is controlled by the pressure control valve 13 (Claim 8).

In any of the above engine-driven compressors 1, the bypass passage 20 is formed as an assembly of a plurality of parallel passages (first and second bypass passages 21 and 22) provided in parallel, By providing parallel flow path solenoid valves (first and second solenoid valves 23 and 24) in each of the parallel flow paths (first and second bypass flow paths 21 and 22), the parallel flow path electromagnetic valves The valves (first and second solenoid valves 23, 24) are used as the flow passage area changing device,
The control device (controller) 30
When the engine is started, the electromagnetic valves for parallel flow paths (first and second electromagnetic valves 23, 24) are all opened,
The discharge pressure increasing process is configured to be executed by sequentially closing at predetermined time intervals while leaving at least one of the parallel flow path solenoid valves (first and second solenoid valves 23 and 24). is also good (claim 9).

Furthermore, in the configuration in which the starting control flow path 51 and the starting pressure regulating valve 52 are provided, a plurality of the starting control flow paths 51 (51a, 51b . . . 51z) are provided, 51z) are provided with electromagnetic valves 53 (53a, 53b, . A starting pressure regulating valve 52 (52a, 52b ... 52z) is provided,
The control device (controller) 30
When the engine is started, all of the solenoid valves 53 (53a, 53b . . . 53z) for the start control flow path are opened,
After closing the bypass flow path 20, the start control flow path electromagnetic valve 53a provided in the start control flow path 51a provided with the start pressure regulating valve 52a having the lowest operating pressure is sequentially closed at predetermined time intervals. , when the warm-up end condition is satisfied, the electromagnetic valve 53z for the starting control flow path provided in the starting control flow path 51z having the starting pressure regulating valve 52z with the highest working pressure is closed. (Claim 10).

With the configuration of the present invention described above, the engine-driven compressor 1 executing the operation control method of the present invention has the following remarkable effects.

Before the end of the warm-up operation, the compressor main body 40 is controlled by performing a discharge pressure increase process in which the pressure in the receiver tank 60 is increased to the refueling start pressure by opening the intake regulating valve 11 to a degree less than full open. By securing the supply amount of lubricating oil necessary for lubrication and cooling, after that, the control of the intake control valve 11 by the pressure control valve 13 is performed due to the satisfaction of the warm-up operation cancellation condition. Also, it is possible to suitably prevent the occurrence of an abnormal rise in the discharge temperature due to insufficient supply of lubricating oil, and it is possible to prevent the occurrence of an emergency stop of the engine-driven compressor due to an abnormal rise in the discharge temperature. rice field.

This discharge pressure increase process raises the pressure in the receiver tank 60 within a predetermined low pressure range with respect to the rated pressure. The load on the engine was smaller than when the pressure was raised to the rated pressure, and even if the discharge pressure increase process was performed during warm-up, the engine could be prevented from stalling.

In addition to the control flow path 12 and the pressure regulating valve 13, a starting control flow path 51 and a starting pressure regulating valve 52 that opens at a pressure lower than that of the pressure regulating valve 13 are provided. In the configuration in which the intake regulating valve 11 is controlled by the starting pressure regulating valve 52 until the operation termination condition is satisfied, the intake regulating valve 11 is controlled by the pressure regulating valve 13 before shifting to normal operation. In addition, the pressure in the receiver tank 60 can be raised from the above-mentioned refueling start pressure to a predetermined starting unload pressure that is higher than the refueling start pressure but lower than the rated pressure. By increasing the amount of oil supplied to the machine main body 40, it was possible to more reliably prevent the occurrence of an abnormal rise in the discharge temperature when the normal operation was started thereafter.

In a configuration in which the discharge pressure increase process is performed in stages, or in a configuration in which a plurality of starting pressure regulating valves 52 with different operating pressures are applied sequentially from the lowest operating pressure, the pressure inside the receiver tank 60 increases as the engine warms up. By increasing the pressure, and thus the back pressure of the compressor body 40, and gradually increasing the load on the engine, the amount of oil supplied to the compressor body 40 before the transition to normal operation can be adjusted to the oil supply during normal operation. Although it is a configuration that can increase to an amount close to the amount, it was possible to suitably prevent the engine from stopping (stall) during warm-up.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is an explanatory diagram of the overall configuration of an engine-driven compressor of the present invention; FIG. 2 is a cross-sectional view showing a configuration example of an intake control valve; FIG. 5 is a cross-sectional view showing a modification of the intake control valve; 1 is a functional block diagram of an engine-driven compressor of the present invention; FIG. FIG. 2 is an explanatory diagram (at normal operation) of the operation of the engine-driven compressor of the present invention; (A) is a time chart showing the operation of each part of the engine-driven compressor during the operation of FIG. 5, and (B) is a graph showing changes in pressure inside the receiver tank. It is an explanatory diagram of the operation of the engine-driven compressor of the present invention (at the time of extreme cold), (A) at the time of starting, (B) at the time of discharge pressure increase processing, (C) at the time of control by the starting pressure adjustment valve, (D ) is an explanatory diagram during normal operation. (A) is a time chart showing the operation of each part of the engine-driven compressor during the operation of FIG. 7, and (B) is a graph showing changes in pressure inside the receiver tank. FIG. 1 is an explanatory diagram of a conventional engine-driven compressor provided with a starting load reduction device (corresponding to FIG. 1 of Patent Document 1); FIG. 2 is an explanatory diagram of an engine-driven compressor provided with a starting load reduction device, where (A) is an explanatory diagram showing the operation of each part during startup, and (B) is an explanatory diagram showing the operation of each part during normal operation; 11. (A) is a time chart showing the operation of each part of the engine-driven compressor during the operation of FIG. 10, and (B) is a graph showing changes in the internal pressure of the receiver tank.

The configuration of the present invention will be described below with reference to the accompanying drawings.

[Overall Configuration of Engine Driven Compressor]
Reference numeral 1 in FIG. 1 denotes an engine-driven compressor of the present invention. This engine-driven compressor 1 includes a compressor body 40, an engine (not shown) for driving the compressor body 40, and the compressor. Equipped with a receiver tank 60 for storing compressed gas discharged from the main body 40. After storing the compressed gas discharged from the compressor main body 40 in the receiver tank 60, it is connected to a service valve 66 via a pressure regulating valve 61. It is configured so that it can be supplied to an air working machine (not shown) or the like.

The compressor main body 40 is an oil-cooled screw compressor that compresses the gas to be compressed together with lubricating oil for lubrication, cooling and sealing. Compressed gas discharged as a gas-liquid mixed fluid is introduced, and it is configured to be able to separate the lubricating oil and the compressed gas in this receiver tank 60, and is collected in the receiver tank 60 An oil supply passage 64 is provided to re-supply lubricating oil to the compressor body 40 via an oil cooler 63 .

[Intake adjustment device]
In the engine-driven compressor 1 configured as described above, the pressure inside the receiver tank 60 approaches a predetermined rated pressure. 9 and 10, it is different from the conventional engine-driven compressor described with reference to FIGS. Same as configuration.

The intake adjusting device 10 also includes an intake adjusting valve 11 that controls the opening and closing of the intake port 41 of the compressor main body 40, and a control flow path 12 that communicates between the closed valve pressure receiving chamber 113 of the intake adjusting valve 11 and the receiver tank 60. , according to the pressure in the receiver tank 60, the control passage 12 is opened when the pressure in the receiver tank 60 is equal to or higher than a predetermined rated pressure, and the control passage 12 is closed when the pressure is less than the rated pressure. 9 and 10, the point that it is constituted by the valve 13 and the point that it is provided with the release passage 14 for releasing the compressed gas in the valve-closing pressure receiving chamber 113 through the throttle 15 will be explained with reference to FIGS. The configuration is similar to that of the engine-driven compressor described above.

[Intake control valve]
The intake control valve 11 that constitutes the intake control device 10 opens and closes the intake port 41 of the compressor body 40 as described above. In this embodiment, the intake control valve 11 shown in FIG. ing.

The intake control valve 11 shown in FIG. 2 has a body (valve box) 111 with a space formed therein that forms an intake passage 115 through which the gas to be compressed passes. By seating the valve element 116 on the valve seat 115a, the suction passage 115 can be closed.

This valve body 116 is a so-called "umbrella valve" in which a valve shaft 116a is attached to a disk-shaped valve body 116, and the valve shaft 116a is inserted into a cylindrical sleeve 117 formed in the body 111. By moving the valve body 116 back and forth in the axial direction of the sleeve 117 in this state, the valve body 116 is moved between the closed position where the valve body 116 is seated on the valve seat 115a and the open position where the valve body 116 is separated from the valve seat 115a. is configured to allow movement of

In order to enable such movement of the valve body 116, a cylinder 112 is formed coaxially with the sleeve 117 in the valve box 111 of the intake control valve 11 and communicates with the intake passage 115 via the sleeve 117. It is

The cylinder 112 forms an airtight chamber with the valve stem 116a inserted into the sleeve 117 and by closing the end portion of the cylinder 112 on the side opposite to the formation side of the sleeve 117 with an end plate 118. The inside of the (cylinder) 112 is divided into two chambers via a pressure receiving body 119, which in this embodiment is a piston, connected to the other end of the valve shaft 116a. A pressure receiving chamber 113 is formed, and an auxiliary pressure receiving chamber 114 is formed on the opposite side of the piston 119 from the valve closing pressure receiving chamber 113 .

In the illustrated configuration, the intake control valve 11 is of the normally open (NO) type. Although the chamber 114 functions as a spring chamber, the spring 114a does not necessarily need to be provided in the auxiliary pressure receiving chamber 114 if the intake control valve 11 can be of a normally open type.

As the intake regulating valve 11, instead of the intake regulating valve 11 having the structure shown in FIG. 2, an intake regulating valve 11 having a structure having a backflow prevention function as shown in FIG. 3 may be employed.

In this configuration, the valve shaft is divided into a valve shaft 116a' provided on the valve body 116 side and a valve shaft 119a provided on the pressure receiving body (piston) 119 side. A spring 116b is provided between the valve shaft 119a on the body (piston) 119 side and biases the valve body 116 toward the valve seat 115a.

The biasing force of the spring 116b keeps the valve body 116 in contact with the valve seat 115a even when the pressure receiving body (piston) 119 is at the valve open position on the left side of the drawing.

The biasing force of this spring 116b is weak, and when the pressure receiving body (piston) 119 is at the valve open position on the left side of the drawing, if the pressure in the suction passage 115 on the secondary side with respect to the valve seat 115a becomes negative pressure, The valve body 116 is separated from the valve seat 115a, and the compressor main body 40 is configured to be able to suck the gas to be compressed.

On the other hand, even when the pressure-receiving body (piston) 119 is at the valve open position on the left side of the paper, if the pressure in the intake passage 115 on the secondary side with respect to the valve seat 115a rises, the valve body 116 will move to the valve seat 115a. Backflow is prevented by being pressed against the

As described above, when the intake regulating valve 11 with a backflow prevention function is employed in the engine-driven compressor 1 of the present invention, even if the valve body 116 is in contact with the valve seat 115a, the valve seat 115a When the pressure in the suction passage on the secondary side of the valve seat 115a becomes lower than the pressure in the suction passage on the primary side, the valve body 116 is separated from the valve seat 115a and the compressor body 40 is closed. is included in the "open" or "open" state of the intake regulating valve 11.

In addition, in the structure of the intake control valve 11 explained with reference to FIGS. 2 and 3, not only the valve body 116 and the valve seat 115a, but also the cylinder 112 and the piston 119 for moving the valve body 116 back and forth are all included. Although the configuration provided in the common body (valve box) 111 is shown, it is not equipped with an intake regulating valve main body without a valve body drive mechanism like the conventional engine-driven compressor described with reference to FIG. , and the drive mechanism such as the unloader regulator for driving the valve body of the intake regulating valve body may be separately provided. A body 119 is formed within the unloader regulator.

Furthermore, in the intake control valve 11 explained with reference to FIGS. Although the partitioning structure is adopted by providing the piston 119 that moves as a pressure receiving body, the pressure receiving body 119 is not limited to the above-mentioned piston, and the operation of the valve body 116 is performed by the compressed gas introduced into the valve closing pressure receiving chamber 113. For example, a diaphragm or the like may be used as the pressure receiving body 119 as long as it can be controlled.

[Bypass flow path]
In addition to the control flow path 12 described above, a bypass flow path 20 is also in communication with the closed valve pressure receiving chamber 113 of the intake regulating valve 11 configured as described above. It is configured such that the compressed gas in the receiver tank 60 can be introduced into the closed valve pressure receiving chamber 113 of the intake regulating valve 11 by bypassing the regulating valve 13 .

The bypass flow path 20 is provided with a flow path area changing device that makes the flow path area of the bypass flow path 20 variable. The opening of the intake control valve 11 can be changed by changing the flow rate of the compressed gas introduced into the closed valve pressure receiving chamber 113 .

In order to make the flow area of the bypass flow channel 20 variable, in the present embodiment, the above-described bypass flow channel 20 is a set of two parallel flow channels (a first bypass flow channel 21 and a second bypass flow channel 22). The first bypass flow path 21 and the second bypass flow path 22 are provided with electromagnetic valves (a first electromagnetic valve 23 and a second electromagnetic valve 24), respectively. The flow area of the bypass flow path 20 is maximum when both are open, and the flow area is narrowed by closing one of the first and second solenoid valves 23 and 24, and the first and second solenoid valves By closing both 23 and 24, the bypass channel 20 can be blocked.

Therefore, in the illustrated embodiment, the first and second solenoid valves 23 and 24 serve as the above-described flow passage area changing device for varying the flow passage area of the bypass flow passage.

In the embodiment shown in FIG. 1, the other end of the common flow path 25, one end of which communicates with the receiver tank 60, is connected to an aluminum alloy block manifold 26 and branched. Although the bypass flow path 21 and the second bypass flow path 22 are communicated at one end and the other end is communicated with the valve closing pressure receiving chamber 113 of the intake control valve 11, the control flow path 12 and the first bypass are shown. One end of the flow path 21 and the second bypass flow path 22 may directly communicate with the receiver tank 60 as shown in FIGS. good.

In this embodiment, the first electromagnetic valve 23 provided in the first bypass flow path 21 described above is a normally open (NO) type electromagnetic valve, and the second electromagnetic valve provided in the second bypass flow path 22 described above Although a normally closed (NC) type solenoid valve is used as 24, it is not limited to this configuration, and various combinations can be used.

1 to 3, reference numeral 27 denotes a three-way solenoid valve, and the C port of this three-way solenoid valve 27 is connected to the auxiliary pressure receiving chamber 114 (spring chamber: FIG. 2 and FIG. 3), the flow path 28a attached to the A port is connected to the intake flow path 115 of the intake control valve 11 on the secondary side of the valve seat 115a, and the flow path 28b attached to the B port is connected to the intake air. It communicates with the primary side of the regulating valve 11 .

As a result, by switching the three-way electromagnetic valve 27, the auxiliary pressure receiving chamber 114 of the intake control valve 11 is selectively communicated with the intake passage 115 on the secondary side of the valve seat 115a and the primary side of the intake control valve 11. configured to be able to

[Starting control flow path]
In the engine-driven compressor 1 of the present invention, the pressure regulating valve 13 provided in the control flow path 12 is bypassed, and the receiver tank 60 and the valve closing pressure receiving chamber 113 of the intake regulating valve 11 are communicated with each other. A control channel 51 may be provided.

The starting control flow path 51 is provided with a starting pressure regulating valve 52 which opens when the pressure in the receiver tank 60 becomes equal to or higher than a predetermined starting unload pressure and closes when the pressure becomes less than the starting unload pressure. In series with the starting pressure regulating valve 52, an electromagnetic valve 53 for a starting control flow path, which is an electromagnetic opening/closing valve [in this embodiment, a normally closed (NC) type electromagnetic opening/closing valve] is provided.

The aforementioned starting unloading pressure is set to a pressure that is higher than the refueling start pressure and lower than the rated pressure. When the bypass flow path 20 is closed while the intake regulating valve 11 is open, the opening/closing control of the intake regulating valve 11 is started by the starting pressure regulating valve 52 whose operating pressure is set lower than that of the pressure regulating valve 13. It is

The start control flow path 51, the start pressure regulating valve 52, and the start control flow path electromagnetic valve 53 are not provided in the engine-driven compressor 1 of standard specifications, for example, and are not provided in the engine-driven compressor 1 of cold region specifications. 1 may be provided.

The starting control flow path 51, the starting pressure regulating valve 52, and the starting control flow path electromagnetic valve 53 may be provided one by one. , 51z are provided in parallel, and starting pressure control valves 52a, 52b, . . . 52z and electromagnetic valves 53a, 53b, .

In this case, the working pressure of each of the starting pressure regulating valves 52a, 52b, . The starting unload pressure can be increased step by step by sequentially closing the solenoid valve for the starting control flow path provided in the starting control flow path where the low starting pressure adjustment valve is installed. good.

[Switches, sensors, etc.]
The engine-driven compressor 1 of the present invention configured as described above is provided with a controller 30, which is a control device for controlling the operation of each part of the engine-driven compressor 1. Switches and sensors for outputting electrical signals are provided (see FIG. 4).

Among these switches, switches for turning on and off the main power supply of the engine-driven compressor 1, starting and stopping the engine, etc. (to be performed by the controller 30 described later) are provided. can be done.

As an example, in the embodiment shown in FIG. 4, a main switch 70 and a starter switch 72 are provided on the operation panel of the engine-driven compressor 1 as such switches.

Among them, the main switch 70 switches between "ON" and "OFF" of the main power supply of the engine-driven compressor 1. In the illustrated embodiment, the main switch 70 has two positions of ON and OFF. A rotary switch is used to switch between

Among these, "OFF" is a stopped state in which the power supply to each part of the engine-driven compressor 1 is stopped, and "ON" is a so-called "accessory position", where the engine, the electronic control device such as the controller 30, This is a state in which power is supplied to various sensors, instruments, and the like.

In addition, the start switch 72 is a switch for starting the engine, and in this embodiment, it is composed of a push-button type switch. The starter motor is energized to start the engine.

In the configuration of the engine-driven compressor 1 having such a main switch 70 and a start switch 72, after rotating the main switch 70 from the "OFF" position to the "ON" position, the start switch 72 is pressed for a long time. By starting the engine, the engine-driven compressor 1 can be started and continued to operate. 1 can be stopped.

The switch for starting and stopping the engine-driven compressor 1 is not limited to the configuration in which the main switch 70 and the start switch 72 are separately provided as described above, and the accessory (main switch) can be turned on and off. can be performed and the starter motor can be turned on and off, various configurations can be adopted. , By inserting and turning the key, it is possible to switch from the OFF position to the ON position (accessory position) and further to the start position where the engine starter motor is rotated. good.

In addition, the engine-driven compressor 1 of the present invention is provided with a temperature sensor 65 for detecting the oil temperature of the compressor body 40 (FIGS. 1 and 4), and the controller 30 receives the temperature from this temperature sensor 65. A change in the oil temperature of the compressor body 40 is monitored based on the detection signal.

〔controller〕
In the engine-driven compressor 1 of the present invention configured as described above, the operation of the switches described above, the change in the oil temperature of the compressor main body 40 detected by the temperature sensor 65, and the built-in timer 36 A controller 30, which is an electronic control device, is provided for controlling the operations of the first solenoid valve 23, the second solenoid valve 24, and the three-way solenoid valve 27 based on the count.

The controller 30 executes the following control based on the operating states of the switches 70 and 72, the discharge temperature of the compressor main body 40 detected by the temperature sensor 65, and the count of the timer 36.

(1) Starting operation When the operator turns the main switch 70 to the "ON" position, each part of the engine-driven compressor 1 is energized and the controller 30 is activated.

Accordingly, the controller 30 receives the temperature detected by the temperature sensor 65 that detects the oil temperature of the compressor body 40 and determines whether the oil temperature is 0° C. or less.

If the oil temperature is higher than 0°C, the controller 30 further determines whether the oil temperature is 60°C or lower. Elapsed operation time (180 seconds from the start of the engine as an example) is the condition for canceling the warm-up operation, and if the oil temperature of the compressor body exceeds 60 ° 60 seconds after starting is set as a warm-up cancellation condition.

After that, when the engine is started by pressing the start switch 72 for a long time, the controller 30 energizes the solenoid valve 53 (NC type in this embodiment) for the start control flow path when the oil temperature exceeds 0°C. is not performed, the start control flow path 51 is kept closed, and the first solenoid valve 23 is de-energized (OFF), that is, while the second solenoid valve 24 is kept open, the second solenoid valve 24 is energized (ON). and open, and in this state, the starter motor is rotated to start the engine [see "ENG start" in Figs. 5A and 6].

In this way, the closing valve pressure receiving chamber 113 of the intake control valve 11 is communicated with the receiver tank 60 via the bypass channel 20 (the first and second bypass channels 21 and 22). Even if the control of the intake regulating valve 11 is disabled and the pressure in the receiver tank 60 is less than the operating pressure of the pressure regulating valve 13, the intake regulating valve 11 can be made to close. becomes.

As a result, when the pressure in the receiver tank 60 rises due to the rotation of the compressor body 40 and exceeds the operating pressure of the intake control valve 11, the intake control valve 11 is closed.

As a result, the engine starts to warm up in a no-load state in which the intake regulating valve 11 closes the intake port 41 of the compressor body 40 .

1 and 5, in which the three-way solenoid valve 27 is provided, the controller 30 causes the auxiliary pressure receiving chamber 114 of the intake regulating valve 11 to move to the intake passage 115 on the secondary side of the valve seat 115a when the engine is started. The three-way solenoid valve 27 is switched to a position communicating with the port CA (a position communicating between the ports CA).

As a result, the compressor main body 40 starts rotating along with the engine starting operation, and the inside of the intake passage 115 on the secondary side of the valve seat 115a becomes negative pressure. As a result, the closing operation of the intake control valve 11 can be completed earlier when the engine is started.

(2) Discharge pressure increase process When the controller 30 determines that a predetermined time X (10 seconds in this embodiment as an example) has elapsed after the engine is started based on the count of the timer 36, the first electromagnetic valve 23 is energized. (ON) is started to close the first solenoid valve 23, and energization (ON) to the three-way solenoid valve 27 is started to move the auxiliary pressure receiving chamber 114 of the intake control valve 11 to the intake passage on the primary side of the valve seat 115a. The three-way solenoid valve 27 is switched to the position communicating with 115 (the position communicating between the ports CB) [see "discharge pressure increasing process" in FIGS. 5B and 6].

As a result, the negative pressure in the auxiliary pressure receiving chamber 114 is eliminated, and the introduction of the compressed gas that has been introduced from the receiver tank 60 into the valve closing pressure receiving chamber 113 of the intake control valve 11 via the first bypass passage 21 is stopped. As a result, the flow rate of the compressed gas introduced into the valve closing pressure receiving chamber 113 is reduced, thereby reducing the pressure in the valve closing pressure receiving chamber 113 .

Therefore, the intake control valve 11 changes from a fully closed state to a slightly opened state with a predetermined degree of opening less than fully open, and the compressor body 40 starts intake air, for example, at a gauge pressure of about 0.1 MPa. The pressure in the receiver tank 60, which was already there, rises to the refueling start pressure (for example, about 0.35 MPa in gauge pressure) by this discharge pressure increasing process [see "STEP 2" in FIG. 6B].

In the illustrated embodiment, the bypass channel 20 is formed by two channels consisting of first and second bypass channels 21 and 22, one of which (the first bypass channel 21) is closed to reduce the flow rate of the compressed gas introduced into the closed valve pressure receiving chamber 113 of the intake control valve 11, thereby increasing the pressure in the receiver tank 60 to the refueling start pressure.

On the other hand, for example, the bypass flow path 20 is configured by three or more parallel flow paths, leaving at least one parallel flow path and closing the other parallel flow paths one by one at predetermined time intervals. It is also possible to increase the pressure to a predetermined refueling start pressure.

In this case, even if the refueling start pressure is set to a higher pressure, it is possible to prevent the engine from stalling.

(3) Normal operation The controller 30 uses the lapse of the warm-up operation time (cold operation time or warm operation time) set based on the oil temperature at the start as described above as a condition for canceling the warm-up operation. When the temperature release condition is satisfied, the second solenoid valve 24 is de-energized (turned OFF) to close the second solenoid valve 24, thereby blocking the second bypass flow path 22 [FIGS. 6 "Cancellation of warm-up operation"].

As a result, the introduction of the compressed gas from the receiver tank 60 into the valve closing pressure receiving chamber 113 of the intake control valve 11 through the second bypass passage 22 is stopped.

By completely closing the bypass flow path 20 (21, 22) in this manner, the control of the opening and closing operation of the intake control valve 11 is performed by the pressure control valve 13 provided in the control flow path 12, and normal operation is performed. Transition.

At the time of transition to normal operation, the pressure in the receiver tank 60 is the refueling start pressure, which is a predetermined pressure lower than the rated pressure. Since the compressed gas in the receiver tank 60 is not introduced into the closed valve pressure receiving chamber 113 of the valve 11, the intake control valve 11 is fully opened and the compressor body 40 starts full load operation.

As described above, in the configuration of the present invention, the pressure in the receiver tank 60 is increased to a predetermined oil supply start pressure by the above-described discharge pressure increase process before shifting to normal operation, and the amount of oil supplied to the compressor body 40 is increased. is increased, it is possible to appropriately prevent the occurrence of an abnormal rise in the discharge temperature due to insufficient supply of lubricating oil when the compressor body 40 starts full-load operation after shifting to normal operation. be able to.

[Control when the oil temperature is 0°C or less]
The warm-up operation when the oil temperature exceeds 0°C when the main switch is turned ON has been described above. can be configured to

(1) Starting operation When the engine is started by long-pressing the start switch 72 when the oil temperature is below 0°C, the controller 30 energizes the solenoid valve 53 for the start control flow path. Then, the start control path 51 is opened, and the first solenoid valve 23 is de-energized (OFF), that is, while maintaining the open state, the second solenoid valve 24 is energized (ON) and opened, and in this state, the starter motor to start the engine [see "ENG start" in FIGS. 7A and 8].

In this way, the valve closing pressure receiving chamber 113 of the intake regulating valve 11 is communicated with the receiver tank 60 via the bypass flow path 20 (the first and second bypass flow paths 21 and 22). Even if the receiver tank 60 and the closed valve pressure receiving chamber 113 of the intake regulating valve 11 are in communication with each other through the starting control flow path 51 due to the opening of the electromagnetic valve 53, the intake regulating valve by the starting pressure regulating valve 52 is in a state of communication. 11 is disabled, and even if the pressure in the receiver tank 60 is less than the working pressure of the starting pressure regulating valve 52, the intake regulating valve 11 can be closed. Become.

As a result, when the pressure in the receiver tank 60 rises slightly due to the rotation of the compressor body 40 and exceeds the operating pressure of the intake control valve 11, the intake control valve 11 is closed.

As a result, the engine starts to warm up in a no-load state in which the intake regulating valve 11 closes the intake port 41 of the compressor body 40 .

In addition, in the configuration in which the three-way solenoid valve 27 is provided, the controller 30 is placed at a position (port C- The point that the three-way solenoid valve 27 is switched to the position that communicates between A is the same as the operation when the oil temperature is 0° C. or higher as described above.

(2) Discharge pressure increase process After the engine is started, the controller starts energizing (ON) the first solenoid valve and closes the first solenoid valve after a predetermined time (eg, 10 seconds in this embodiment) has elapsed. At the same time, the energization (ON) of the three-way solenoid valve 27 is started, and the position where the auxiliary pressure receiving chamber 114 of the intake control valve 11 communicates with the suction flow path 115 on the primary side of the valve seat 115a (port CB is communicated position) (see "discharge pressure increasing process" in FIGS. 7B and 8).

As a result, the flow rate of the compressed gas introduced into the closing valve pressure receiving chamber 113 of the intake regulating valve 11 decreases, and the pressure in the closing valve pressure receiving chamber 113 decreases. However, the pressure inside the receiver tank 60 rises to the refueling start pressure as the compressor main body 40 starts to take air ("STEP 2" in FIG. 8(B)). reference〕.

(3) Control by starting pressure regulating valve After a predetermined time Y (30 seconds as an example in this embodiment) has passed since the execution of the discharge pressure increasing process described above, the controller 30 starts the second bypass flow path 22 provided in the second bypass flow path 22. The energization to the second solenoid valve 24 is stopped (OFF), and the second solenoid valve 24 is closed [see FIG. 7(C)].

As a result, the introduction of the compressed gas from the receiver tank 60 into the closed valve pressure receiving chamber 113 via the bypass flow path 20 (21, 22) is completely stopped, so that the opening/closing operation of the intake control valve 11 is controlled by the starting control flow. Control is shifted to the starting pressure regulating valve 52 provided in the path 51 .

The starting pressure regulating valve 52 is designed so that the pressure in the receiver tank 60 is a predetermined high pressure with respect to the refueling start pressure and is opened at a starting unload pressure or higher which is a predetermined low pressure with respect to the rated pressure. The operating pressure is regulated.

Even if the opening/closing operation of the intake regulating valve 11 shifts to control by the starting pressure regulating valve 52 due to the blockage of the bypass passage 20 (21, 22), at this point the pressure in the receiver tank 60 is higher than the starting unload pressure. Therefore, when the bypass passage 20 is blocked, the introduction of the compressed gas into the closed valve pressure receiving chamber 113 of the intake regulating valve 11 is stopped and the intake regulating valve 11 is fully opened.

As a result, the full-load operation of the compressor body 40 is started, and the pressure in the receiver tank 60 rises [see "STEP 3" in FIG. 8(B)].

When the pressure in the receiver tank 60 rises above the starting unload pressure, the starting pressure regulating valve 52 opens, and the compressed gas from the receiver tank 60 is introduced into the closed valve pressure receiving chamber 113 of the intake regulating valve 11 to adjust the intake air. Valve 11 closes and the pressure in receiver tank 60 is held near the starting unload pressure.

After the second solenoid valve 24 is closed, the controller 30 stops (turns off) the energization of the start control flow path solenoid valve 53 after a predetermined time (140 seconds in this embodiment as an example) has passed, and the start control is performed. The channel 51 is closed.

As a result, the opening/closing control of the intake regulating valve 11 by the starting pressure regulating valve 52 is completed, and the control shifts to normal control in which the opening/closing control of the intake regulating valve 13 is performed by the pressure regulating valve 13 provided in the control flow path 12 .

In this way, when the engine-driven compressor 1 is started at a predetermined low oil temperature (0° C. or lower as an example), after the bypass flow path 20 is closed, the starting pressure regulating valve provided in the start control flow path 51 By shifting to the control by 52, the pressure in the receiver tank 60 could be increased in multiple steps to the starting unload pressure, which is higher than the refueling start pressure.

As a result, since the outside air temperature is low and the viscosity is high, a sufficient amount of lubricating oil to be supplied to the compressor main body 40 cannot be ensured simply by increasing the pressure in the receiver tank 60 to the lubricating start pressure. Even so, it is possible to supply a sufficient amount of lubricating oil to the compressor main body 40 before shifting to normal operation.

In the above description, a configuration example in which a single starting control flow path 51 is provided has been described. However, as shown as a modification in FIG. 51b . . . 51z may be provided.

In this case, starting pressure regulating valves 52a, 52b, . shall be different.

. . 52z are connected in series with the respective starting pressure regulating valves 52a, 52b . . . 52z. - Provide 53z.

After the bypass flow path 20 is closed, the controller 30 controls the starting control flow path electromagnetic valve 53a provided in the starting control flow path 51a provided with the starting pressure regulating valve 52a having the lowest operating pressure at predetermined time intervals. It closes sequentially, and when the warm-up end condition is satisfied, the electromagnetic valve 53z for the starting control flow path provided in the starting control flow path 51z provided with the starting pressure regulating valve 52z with the highest operating pressure is closed. By configuring as above, the pressure in the receiver tank 60 may be configured to be increased in multiple steps.

Reference Signs List 1 engine-driven compressor 10 intake regulator 11 intake regulator valve 111 body (valve box)
112 airtight chamber (cylinder)
113 Valve closing pressure receiving chamber 114 Auxiliary pressure receiving chamber (spring chamber)
114a spring 115 intake channel 115a valve seat 116 valve body 116a, 116a' valve shaft 116b spring 117 sleeve 118 end plate 119 pressure receiving body (piston)
119a valve shaft 12 control channel 13 pressure regulating valve 14 relief channel 15 throttle 20 bypass channel 21 first bypass channel (parallel channel)
22 second bypass flow path (parallel flow path)
23 first solenoid valve (parallel flow path solenoid valve)
24 Second solenoid valve (parallel flow path solenoid valve)
25 common flow path 26 block manifold 27 three-way solenoid valve 28a to 28c flow path 30 controller (control device)
36 timer 40 compressor body 41 intake port 51 (51a, 51b...51z) starting control flow path 52 (52a, 52b...52z) starting pressure regulating valve 53 (53a, 53b...53z) starting control flow Road solenoid valve 60 Receiver tank 61 Pressure regulating valve 62 Discharge channel 63 Oil cooler 64 Oil supply channel 65 Temperature sensor 66 Service valve 70 Main switch 72 Start switch 300 Engine-driven compressor 310 Intake adjusting device 311 Intake adjusting valve 312 Control Flow path 313 Pressure regulating valve 314 Relief flow path 315 Throttle 316 Unloader regulator 320 Starting load reduction device 321 Bypass flow path 325 Bypass valve 340 Compressor main body 341 Intake port 350 Engine 360 Receiver tank 363 Oil cooler 364 Oil supply flow path 366 Oil separator 367 oil filter

Claims (10)

An engine, an oil-cooled compressor body driven by the engine, a gas-liquid mixed fluid of compressed gas and lubricating oil discharged by the compressor body is introduced to separate the compressed gas and lubricating oil, and the separated A receiver tank that supplies lubricating oil to the compressor body using internal pressure, an intake adjustment valve that controls intake air to the compressor body, and a closing pressure receiving chamber of the intake adjustment valve that communicates with the receiver tank. When the pressure in the control channel and the receiver tank is equal to or higher than a predetermined rated pressure, the control channel is opened, and when the pressure in the receiver tank is lower than the rated pressure, the control channel is closed, thereby opening and closing the intake control valve. A method for controlling the operation of an engine-driven compressor having a pressure regulating valve to control,
Invalidating the control of the intake air regulating valve by the pressure regulating valve, closing the air intake regulating valve when the engine starts, and starting warm-up,
After the engine is started and before a predetermined warm-up end condition is satisfied, the pressure in the receiver tank is reduced to a predetermined level with respect to the rated pressure by opening the intake control valve to a predetermined degree of opening less than full opening. Perform discharge pressure increase processing to increase the lubrication start pressure, which is a low pressure,
The operation of an engine-driven compressor, characterized in that, when the warm-up operation end condition is satisfied, the warm-up operation is ended and the pressure control valve controls the intake air control valve to shift to normal operation. control method. A bypass passage bypassing the pressure regulating valve and communicating between the receiver tank and the closed valve pressure receiving chamber of the intake regulating valve is provided, and the closing of the receiver tank and the intake regulating valve is provided via the bypass passage. By starting the engine in a state in which the valve pressure receiving chambers are communicated, the control of the intake control valve by the pressure control valve is invalidated, and the intake control valve is closed when the engine is started,
performing the discharge pressure increasing process by throttling the flow rate of the compressed gas introduced into the valve closing pressure receiving chamber of the intake control valve through the bypass passage;
2. The engine-driven compressor according to claim 1, wherein the warm-up operation is ended by closing the bypass flow path, and the normal operation is performed in which the intake control valve is controlled by the pressure control valve. operation control method. a starting control flow path that bypasses the pressure control valve and communicates between the closed valve pressure receiving chamber of the intake control valve and the receiver tank;
opening the start control flow path when the pressure in the receiver tank is a predetermined high pressure with respect to the refueling start pressure and is equal to or higher than a start unload pressure, which is a predetermined low pressure with respect to the rated pressure; a starting pressure regulating valve that controls opening and closing of the intake control valve by closing the starting control flow path when the starting unload pressure is less than the starting unload pressure;
After the discharge pressure increasing process, before the warm-up end condition is satisfied, the starting pressure regulating valve controls the intake regulating valve,
When the condition for ending the warm-up operation is satisfied, the control of the intake regulating valve by the starting pressure regulating valve is terminated, the warm-up operation is terminated, and the intake regulating valve is controlled by the pressure regulating valve. 2. The operation control method for an engine-driven compressor according to claim 1, wherein said operation is shifted to said normal operation. A bypass passage bypassing the pressure regulating valve and communicating between the receiver tank and the closed valve pressure receiving chamber of the intake regulating valve is provided, and the closing of the receiver tank and the intake regulating valve is provided via the bypass passage. By starting the engine with the valve pressure receiving chambers communicated, the control of the intake control valve by the pressure control valve and the starting pressure control valve is invalidated, and the intake control valve is closed when the engine is started. ，
performing the discharge pressure increasing process by throttling the flow rate of the compressed gas introduced into the valve closing pressure receiving chamber of the intake control valve through the bypass passage;
4. The engine-driven compressor according to claim 3, wherein after a predetermined time has passed since said discharge pressure increasing process, said bypass passage is closed and control of said intake regulating valve by said starting pressure regulating valve is started. operation control method. The operation control method for an engine-driven compressor according to any one of claims 1 to 4, wherein the discharge pressure increasing process is performed while increasing the degree of opening of the intake control valve stepwise. A plurality of the starting control flow paths are provided, the starting pressure regulating valve is provided in each of the starting control flow paths, and operating pressures of the respective starting pressure regulating valves are set to different pressures,
After the discharge pressure increasing process, the control of the intake control valve by the starting pressure control valve until the condition for ending the warm-up operation is satisfied is controlled by the starting pressure control valve having the lowest operating pressure among the plurality of starting pressure control valves. 4. The method of controlling the operation of an engine-driven compressor according to claim 3, wherein the operating pressure is sequentially switched from the operating pressure to the higher operating pressure at predetermined time intervals. An engine, an oil-cooled compressor body driven by the engine, a gas-liquid mixed fluid of compressed gas and lubricating oil discharged by the compressor body is introduced to separate the compressed gas and lubricating oil, and the separated A receiver tank that supplies lubricating oil to the compressor body using internal pressure, an intake adjustment valve that controls intake air to the compressor body, and a closing pressure receiving chamber of the intake adjustment valve that communicates with the receiver tank. When the pressure in the control channel and the receiver tank is equal to or higher than a predetermined rated pressure, the control channel is opened, and when the pressure in the receiver tank is lower than the rated pressure, the control channel is closed, thereby opening and closing the intake control valve. In engine-driven compressors with pressure regulating valves controlling
a bypass passage that bypasses the pressure regulating valve and communicates between the receiver tank and the closed valve pressure receiving chamber of the intake regulating valve;
a channel area changing device that makes the channel area of the bypass channel variable;
A control device for controlling the flow path area changing device is provided,
By the control device controlling the flow path area changing device,
When the engine is started, by maximizing the flow area of the bypass flow path, the intake control valve is closed at the same time as the engine is started, and warm-up operation is started;
After the engine is started and before a predetermined warm-up end condition is satisfied, the receiver is opened by reducing the flow area of the bypass flow path and opening the intake control valve to a predetermined opening degree that is less than fully open. In addition to performing a discharge pressure increase process for increasing the pressure in the tank to the refueling start pressure, which is a predetermined lower pressure than the rated pressure,
When the warm-up end condition is satisfied, the bypass flow path is closed to end the warm-up operation, and the pressure control valve controls the intake control valve to shift to normal operation. engine driven compressor. An engine, an oil-cooled compressor body driven by the engine, a gas-liquid mixed fluid of compressed gas and lubricating oil discharged by the compressor body is introduced to separate the compressed gas and lubricating oil, and the separated A receiver tank that supplies lubricating oil to the compressor body using internal pressure, an intake adjustment valve that controls intake air to the compressor body, and a closing pressure receiving chamber of the intake adjustment valve that communicates with the receiver tank. When the pressure in the control channel and the receiver tank is equal to or higher than a predetermined rated pressure, the control channel is opened, and when the pressure in the receiver tank is lower than the rated pressure, the control channel is closed, thereby opening and closing the intake control valve. In engine-driven compressors with pressure regulating valves controlling
a bypass flow path and a start control flow path that bypass the pressure regulating valve and communicate between the receiver tank and the closed valve pressure receiving chamber of the intake regulating valve;
a channel area changing device that makes the channel area of the bypass channel variable;
The start control flow path that opens when the pressure on the discharge side of the compressor body is equal to or higher than the starting unload pressure, which is a predetermined lower pressure than the rated pressure, and closes when the pressure is less than the starting unload pressure. A starting pressure regulating valve provided in
a starting control flow path electromagnetic valve provided in the starting control flow path and communicating in series with the starting pressure regulating valve;
A control device for controlling the flow path area changing device and the solenoid valve for the start control flow path,
The control device is
When the engine is started, the solenoid valve for the start control flow path is opened and the flow path area changing device is operated to maximize the flow path area of the bypass flow path, thereby adjusting the intake air when the engine is started. Close the valve and start warm-up,
After the engine is started and before a predetermined warm-up termination condition is satisfied, the flow passage area changing device is controlled to reduce the flow passage area of the bypass flow passage so that the intake control valve is opened to a predetermined value less than fully open. By opening the receiver tank to an opening of , a discharge pressure increase process is performed in which the pressure in the receiver tank is increased to a refueling start pressure that is a predetermined lower pressure than the start unload pressure,
After the discharge pressure increasing process, the bypass flow path is closed before the warm-up end condition is satisfied, and the control of the intake control valve by the starting pressure control valve is started,
When the condition for terminating the warm-up operation is satisfied, the electromagnetic valve for the starting control flow path is closed to end the control of the intake regulating valve by the starting pressure regulating valve, the warm-up operation is ended, and the pressure regulating valve An engine-driven compressor characterized by shifting to normal operation in which the intake control valve is controlled by By forming the bypass flow path as an aggregate of a plurality of parallel flow paths and providing a parallel flow path solenoid valve in each of the parallel flow paths, the parallel flow path electromagnetic valve The valve is the flow path area changing device,
the controller,
When the engine is started, all of the solenoid valves for parallel flow paths are opened;
9. The engine-driven compressor according to claim 7, wherein the discharge pressure increasing process is executed by sequentially closing at predetermined time intervals with at least one of the parallel flow path solenoid valves left. A plurality of the start control flow paths are provided, each of the start control flow paths is provided with a start control flow solenoid valve for opening and closing the start control flow path, and a start pressure adjustment valve with a different operating pressure,
the controller,
When the engine is started, all of the solenoid valves for the start control flow path are opened, and
After closing the bypass flow path, the electromagnetic valve for the starting control flow path provided in the starting control flow path provided with the starting pressure regulating valve with the lowest operating pressure is sequentially closed at predetermined time intervals, and the warm-up 9. The solenoid valve for the starting control flow path provided in the starting control flow path provided with the starting pressure regulating valve having the highest operating pressure is closed when the operation termination condition is satisfied. Engine driven compressor.

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