JPH0428866Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an improvement of a compressor, particularly its suction valve, and relates to a compressor that is effective for use in, for example, an air brake device of a vehicle such as an automobile.

[Conventional technology]

As a compressor used in the air brake system of vehicles such as automobiles, the compressor opens and closes a cylinder chamber, a piston that is slidably fitted in the cylinder chamber and reciprocated by a drive device, and an intake passage that communicates with the cylinder chamber. It is equipped with a suction valve and a discharge valve that opens and closes a discharge passage communicating with a cylinder chamber, and the suction valve has a disk-shaped valve body (disk valve) that moves into and out of the valve seat in a direction perpendicular to the valve seat. Some valves are configured to open and close the valve port.

In such a compressor, it is desirable that the lift amount of the disc valve in the suction valve be set as large as possible in order to increase suction efficiency. However, since the maximum value of the disc valve is restricted due to its strength during high-speed operation, the lift amount of the disc valve in the intake valve is set to be small enough to correspond to the high-speed operation.

[Problem that the invention attempts to solve]

In such a compressor, the lift amount of the disk valve in the suction valve is set to be small to correspond to high-speed operation, resulting in low suction efficiency.

Therefore, efforts have been made to ensure high efficiency by installing a compressor that operates when the engine rotates at high speeds and a compressor that operates when the engine rotates at low speeds. would be contrary to the requirements of

An object of the present invention is to provide a compressor that can ensure high suction efficiency and predetermined strength in both high-speed and low-speed operation.

[Means for solving problems]

The compressor according to the present invention includes a cylinder chamber,
A piston that is slidably fitted in the cylinder chamber and reciprocated by a drive device, a suction valve that opens and closes a suction passage communicating with the cylinder chamber, and a discharge valve that opens and closes a discharge passage that communicates with the cylinder chamber. The compressor includes a detection means for detecting the operating speed of the drive device, and an actuator that operates when the detection means detects the operating speed of the drive device, and the actuator operates to lift the valve body of the suction valve. It is characterized by being configured to adjust the amount.

[Effect]

According to the above-mentioned means, the lift amount of the valve body of the suction valve is adjusted by the actuator in accordance with the operating speed of the drive device, so that the lift amount of the valve body during high-speed operation is reduced, so that the lift amount of the valve body during low-speed operation is reduced. By setting the lift amount of the valve body to be large during high-speed operation, maximum suction efficiency can be ensured within a range that does not exceed the strength of the valve body, and during low-speed operation, the lift amount of the valve body can be set to be large. Maximum suction efficiency can be ensured without being restricted by the strength of the valve body.

〔Example〕

FIG. 1 is an enlarged partial vertical cross-sectional view of a compressor that is an embodiment of the present invention, and FIG. 2 is a schematic diagram showing an air brake device in which this compressor is used.

In this embodiment, this compressor supplies compressed air (hereinafter referred to as air) to the air brake device 1.
It is configured to supply Although detailed description is omitted, the air brake device 1 includes an engine 2 for driving the vehicle, an air cleaner 3 for supplying clean air to the engine 2, a flywheel 4 that rotates in synchronization with the engine 2, and a brake. An actuating device 5, a reservoir 6 for supplying air to the brake actuating device 5, and a check valve 7 interposed between the reservoir 6 and the compressor.
, an unload valve 8 connected to the compressor, and a pressure regulator 9 for controlling the unload valve 8.

In this embodiment, the compressor 11 is configured to be reciprocating and includes a cylinder body 12. A cylinder chamber 13 is formed in the main body 12, and a piston 14 is fitted into the cylinder chamber 13 so as to be able to freely reciprocate and slide. The piston 14 is configured to be linearly driven back and forth by the engine 2, and therefore, the engine 2 substantially constitutes a drive device for driving the compressor 11. A cylinder head 15 is attached to one end (hereinafter referred to as the upper end side) of the cylinder chamber 13.
A discharge port and a suction port are provided in the cylinder head 15 so as to communicate with the cylinder chamber 13, respectively. A discharge passage 17 is connected to the discharge port 16, and a discharge valve 18 is interposed between the discharge port 16 and the discharge passage 17 inside the cylinder head 15 so as to open and close the flow. The discharge passage 17 is connected to the reservoir 6 via the check valve 7, and a relief valve 8 is also connected to the discharge passage 17.

On the other hand, a suction passage 20 is connected to the suction port 19 , and the suction passage 20 is connected to the air cleaner 3 . A suction valve 21 is disposed inside the cylinder head 15 between the suction port 19 and the suction passage 20 to open and close the flow passage. The suction valve 21 includes a valve sleeve 22 screwed into the cylinder head 15, and a valve chamber 23 substantially formed by a hollow portion of the valve sleeve 22 communicates with the suction port 19. A disc valve 24 as a valve body of the suction valve 21 is inserted into the valve chamber 23 so as to be movable in the direction of the cylinder center.
4 is always urged upward by a valve spring 25.

Inside the cylinder head 15, a cylinder device 26 as a control actuator is provided above the suction valve 21. That is, inside the cylinder head 15, a cylinder chamber 27 of a cylinder device 26 is arranged above and concentrically with the valve cylinder 22, and a piston 28 is disposed in the cylinder chamber 27 within a predetermined stroke range. They are slidably fitted. The upper limit of the piston 28 is regulated by a plug 29 screwed into the upper end surface of the cylinder head 15, and the lower limit thereof is regulated by a stopper portion 30 formed on the upper end surface of the valve cylinder 22. Further, the piston 28 is always pressed to the upper limit position by a spring 31 which exerts a reaction force on the valve cylinder 23. A valve passage 32 is formed inside the piston 28, and a valve seat 33 is formed on the lower end surface of the piston 28 so as to surround a valve port substantially formed by the lower end opening of the valve passage 32. The disc valve 24 of the suction valve 21 is pressed against the valve seat 33 by the urging force of a valve spring 25. A valve hole 34 is provided at the upper end of the piston 28 so that the valve passage 32 and the suction passage 20 can be communicated with each other at all times.

Further, a control port 35 is opened in the plug 29 that closes the control cylinder chamber 27 so as to open into the cylinder chamber 27, and as shown in FIG. A pressure regulator 9 is connected via a normally closed on-off control valve 36. A controller 37 is connected to this control valve 36.
A rotation sensor 38 that substantially detects the rotation speed of the engine 2 by detecting the rotation speed of the flywheel 4 is connected to the engine. The controller 37 is configured to open and operate the control valve 36 when the rotation sensor 38 detects a high rotation speed higher than a preset rotation speed.

Next, the action will be explained.

When the piston 14 is moved from the top dead center to the bottom dead center in the cylinder chamber 13, the disc valve 24 of the suction valve 21 moves away from the valve seat 33, and the valve passage 32 is opened, so that air is sucked in. It is sucked into the cylinder chamber 13 via the passage 20 → valve hole 34 → valve passage 32 → suction port 19. In the reverse compression stroke, the suction valve 21 is closed, and when the internal pressure of the cylinder chamber 13 reaches a predetermined pressure, the discharge valve 18 is opened, so that high-pressure air flows into the discharge port 16.
→It is supplied to the reservoir 6 via the discharge path 17.

The air in the reservoir 6 is supplied to the brake actuating device 5 when the brake is applied under the control of a brake valve (not shown).
is supplied as appropriate to activate it.

When the internal pressure of the reservoir 6 increases and reaches a set value, this is detected by the pressure regulator 9 and the air in the reservoir 6 is supplied to the unload valve 8. As a result, the unload valve 8 is opened, so that the pressure from the discharge passage 17 is released to the atmosphere. As a result, the load on the engine 2 for driving the compressor 11 is reduced.

In the compression action of the compressor 11 mentioned above, when the engine 2 rotates at low speed, the controller 3
7, the control valve 36 is closed. Therefore, the piston 28 in the cylinder device 26, which serves as an actuator for adjusting the lift amount of the disc valve 24, is pushed up to the upper limit position by the spring 31.

Therefore, when the engine is rotating at low speed, the disc valve 24 has the maximum lift amount and is pushed toward the valve seat 33.
Since the suction efficiency is extremely high, the suction efficiency is extremely high.

Here, in order to increase the suction efficiency of the suction valve,
It is desirable to set the lift amount of the disc valve 24 of the suction valve 21 to be large. Therefore, in this embodiment, the lift amount of the disc valve 24 during low-speed rotation is set to be larger than that during high-speed rotation.

When the engine 2 reaches a high speed rotation region equal to or higher than a preset rotation speed, the rotation sensor 38 detects this. Based on this detection, the control valve 36 is opened by the controller 37.
The air in the reservoir 6 is transferred to the pressure regulator 9→
It is supplied to the upper chamber of the piston 28 in the cylinder chamber 27 via the control valve 36 and the control port 35 . As a result, the piston 28 is lowered to the lower limit position regulated by the stopper portion 30.

In this way, when the piston 28 is positioned at the lower limit, the valve seat 33 formed on the lower end surface of the piston 28 is lowered relative to the valve chamber 23, so the lift amount of the disc valve 24 is reduced. will be done.

By the way, when the engine is operating at high speed, the reciprocating movement of the piston in the compressor 11 driven by the engine also becomes high speed, and accordingly, the frequency of seating and separation of the disk valve 24 in the intake valve 21 and the impact thereof become more severe. Therefore, if the lift amount of the disc valve 24 during high-speed rotation is set too large, the impact force etc. applied to the disc valve will increase, resulting in a risk in terms of strength.
As a result, the setting of the lift amount of the disc valve is
This is limited by the strength of the disc valve during high speed rotation. In other words, it is necessary to set the lift amount of the disc valve small to match the strength of the disc valve during high-speed operation. However, if the lift amount is set small, the opening amount of the valve seat will be small, resulting in poor suction efficiency during low speed rotation.

However, in this embodiment, since the lift amount of the disc valve 24 is reduced when the engine rotates at high speed, the impact force acting on the disc valve 24 is suppressed to a small level. Therefore, in terms of strength, no trouble will occur to the disk valve 24. At this time, when the engine rotates at high speed, the speed of compression and suction in the compressor 11 becomes high, so that the suction efficiency also becomes good.

On the other hand, when the engine rotates at low speed, the lift amount of the disc valve 24 becomes large, as described above, so that the suction efficiency becomes good. At this time, since the frequency of seating and seating of the disc valve 24 and its impact are gentle, even if the lift amount of the disc valve 24 is large, the impact force acting on the disc valve 24 is small. Therefore, in terms of strength, no trouble will occur to the disk valve 24.

It should be noted that the present invention is not limited to the above-mentioned embodiments, and may be modified without departing from the gist thereof.
It goes without saying that various changes are possible.

For example, as an actuator for adjusting the lift amount of the valve body of the suction valve, the cylinder device according to the above configuration is not limited to the use, but other cylinder devices, electromagnetic plunger devices, etc. may be used.

The means for detecting the high-speed operating state of the compressor is not limited to a rotation sensor that detects the rotational speed of the engine, but may also be a sensor that directly detects the rotational speed of the compressor.

In the above embodiment, the case where the compressor is used in an air brake device has been described, but the present invention is not limited to this, but can be applied to all compressors such as a compressor used in an air conditioner.

[Effects of the invention] As explained above, according to the invention, the lift amount of the valve body of the intake valve can be set small during high-speed operation, and set large during low-speed operation. Maximum suction efficiency can be obtained in both operating regions, and desired safety can be ensured with respect to the strength of the valve body.

[Brief explanation of the drawing]

FIG. 1 is an enlarged partial vertical sectional view of a compressor according to a first embodiment of the present invention, and FIG. 2 is a schematic diagram showing an air brake device in which this compressor is used. 1... Air brake device, 2... Engine (drive device), 3... Air cleaner, 4... Flywheel, 5... Brake actuation device, 6... Reservoir, 7... Check valve, 8... Unloading valve, 9
...pressure regulator, 11 ... compressor, 12 ... cylinder body, 13 ... cylinder chamber, 14 ... piston, 15 ... cylinder head, 16 ... discharge port, 17 ... discharge path, 18 ……
Discharge valve, 19... Suction port, 20... Suction path, 21
... Suction valve, 22 ... Valve cylinder, 23 ... Valve chamber, 24
... Disk valve (valve body), 25 ... Valve spring, 26 ... Control cylinder device (actuator), 27 ... Cylinder chamber, 28 ... Piston, 29 ... Plug, 30 ... Stopper part, 3
1... Spring, 32... Valve passage, 33... Valve seat, 34... Valve hole, 35... Control port, 36...
... Opening/closing control valve, 37... Controller, 38...
Rotation sensor.

Claims (1)

[Scope of utility model registration request] A cylinder chamber, a piston that is slidably fitted into the cylinder chamber and reciprocated by a drive device, a suction valve that opens and closes a suction passage that communicates with the cylinder chamber, and a discharge passage that communicates with the cylinder chamber. A compressor equipped with a discharge valve includes a detection means for detecting the operating speed of the drive device, and an actuator that operates when the detection means detects the operating speed of the suction valve. A compressor characterized by being configured to adjust the amount of lift of a valve body.