JPH0117672Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] This invention relates to an improvement of a rotary gas compressor used in car coolers and the like.

[Conventional technology]

A gas compressor for a general car cooler is installed in parallel with an automobile engine, is rotationally driven from the engine's crankshaft pulley via a V-belt, and is connected to the drive side by an electromagnetic clutch attached to the compressor side.

Therefore, the capacity of the gas compressor increases almost proportionally to the rotational speed of the automobile engine.

[The problem that the idea attempts to solve]

This causes the air conditioner to work too hard when the car is running at high speed for long periods of time, causing the interior of the car to become overcooled, and the power consumption of the gas compressor to increase more than necessary. let

In order to prevent overcooling as described above, the electromagnetic clutch is configured to control the operation of the gas compressor on and off based on the output of a temperature sensor installed in the evaporator, etc. There is. However, such a configuration causes problems such as frequent engagement and disconnection of the electromagnetic clutch, which causes severe wear and tear on the clutch, and increases engine load fluctuations.

This idea was created in view of the conventional problems mentioned above, and its purpose is to control the amount (pressure) of gas sucked into the cylinder chamber of a gas compressor by simply adding a simple configuration. An object of the present invention is to provide a gas compressor in which an increase in work capacity and power consumption in a high-speed rotation drive range is automatically suppressed.

[Means to solve the problem]

In order to achieve the above object, this invention provides a gas compressor having a rotor and vanes slidable in the radial direction of the rotor in a cylinder chamber, and an inlet for introducing gas into the gas compressor. A circulation hole is formed in the cylinder that communicates with an intake port that passes through the interior and exterior of the cylinder, and a spool is mounted in the circulation hole with one end facing the intake port and biased toward the intake port by a spring. The present invention is characterized in that the gas sucked into the cylinder chamber is received at one end of the spool, and as the flow velocity of the gas increases, the opening degree of the intake port decreases, forming a throttle valve mechanism.

[Effect]

According to the above means, when the rotor rotates at high speed and the flow velocity of gas flowing into the cylinder chamber from the intake port increases, one end surface of the spool is pressed by the gas, and the spool moves against the biasing force of the spring. , the opening degree of the intake port is reduced in accordance with the gas flow velocity, and the amount of gas sucked into the cylinder chamber is controlled to decrease.

〔Example〕

Hereinafter, embodiments of this invention will be described in detail based on the drawings.

Figures 1 and 2 show a rotary gas compressor to which this invention is applied. This gas compressor includes a compressor main body 1, a casing 2 with an open end that surrounds the compressor main body 1, and a front head 3 attached to the open surface of the casing 2.

The compressor body 1 includes a cylinder 4 having an elliptical inner circumference.
It has a front side block 5 and a rear side block 6 attached to both sides of the cylinder 4, and these form an elliptical cylinder chamber. A solid cylindrical rotor 9 equipped with two vanes 8 is horizontally suspended so as to be freely rotatable.

When the rotor 9 is rotationally driven in the direction of arrow A in FIG.
The low-pressure gas introduced from 0 passes through the circulation hole 11 formed in the front side block 5 and the circulation hole 12 formed in the cylinder 4, as shown by the solid line arrow in FIG. sucked into the room. Further, the high pressure gas compressed in the cylinder chamber is discharged from the discharge port 14 and the discharge valve 15 into the gap between the outer periphery of the cylinder 4 and the inner periphery of the casing 2, and is further discharged through the insertion hole ( The oil is supplied to the oil separator 16 at the back of the block 6 through the oil separator 16 (not shown), and is discharged to the outside from the rear space of the casing 2 through the outlet 17, as shown by the broken line arrow in FIG.

Next, the configuration of the intake path, which is the main part of this invention, will be explained in detail.

The intake path of the cylinder 4 consists of a communication hole 12 formed in the axial direction of the cylinder 4, and two intake ports 13, 13 that are opened from the communication hole 12 toward the cylinder chamber. A spool 18 and a spring 19 are attached to the spool 18, and the end face of the spool 18 is pressed by the gas according to the gas flow rate at which the gas sucked into the cylinder chamber flows into the circulation hole 12, thereby forming a throttle valve mechanism that operates. There is.

As shown in FIGS. 2 and 3, the flow holes 12
is formed in a shape in which a circular hole portion 12a and an oval hole portion 12b overlap, and the intake port 1
3 is inserted so as to cross both the circular hole 12a and the oval hole 12b. The spool 18 is slidably inserted into the circular hole 12a, and the opening degree of the intersection opening between the circular hole 12a and the intake port 13 (hereinafter referred to as the valve opening degree) depends on the position of the spool 18. and change.

The spool 18 is constantly urged in the direction of arrow B (FIG. 3) by a spring 19, and
It is pushed in the direction of arrow c by the pressure of the gas that enters through the flow hole 11 of the front side block 5 and is sucked into the cylinder chamber. As the rotational speed of the rotor increases, the amount of gas sucked into the cylinder chamber per unit time increases, that is, the gas flow rate flowing through the circulation hole 12 increases, and accordingly, the gas flows from the intake port 10 to the circulation hole 12. The flow velocity of the gas flowing in also increases, and the force pressing the spool 18 in the direction of arrow c (FIG. 3) also increases.

And, as shown in FIG. 1 and FIG. 3A,
When the spool 18 is located at the rightmost position due to the force of the spring 19, the above-mentioned valve opening is large;
``On the other hand, as the rotational speed of the rotor increases,
As shown in FIG. 3B, the spool 18 is displaced in the direction of arrow c, and the valve opening degree gradually decreases.

Then, the spool stops at a position where the pressing force of the spring and the force pressing the spool in the direction of arrow c are balanced. When the rotor returns to its original speed, the spool is returned by spring pressure. In other words, the spool operates according to the rotational speed of the rotor, and changes the valve opening degree of the intake port 13. ” Furthermore, even if the above-mentioned valve opening becomes completely zero, the intake path inside the cylinder chamber will not be cut off.
Regardless of the position of the spool 18, the oval hole 12
b and the intake port 13 is maintained. This intake path is called the minimum intake opening. In other words, the opening degree of the intake passage passing through the inside and outside of the cylinder 4 gradually decreases within a certain range as the gas flow rate sucked into the cylinder chamber increases.

As is clear from the above explanation, as the rotational speed of the rotor 9 increases, the amount of gas sucked into the cylinder chamber per unit time increases, and as the gas velocity increases, the flow velocity flowing into the flow holes also increases. death,
Since the spool 18 is displaced by the pressing force of the gas, the opening degree of the intake path leading into the cylinder chamber gradually decreases in accordance with the rotational speed of the rotor.As a result, the efficiency of suction into the cylinder chamber decreases, and the rotation The increase in work capacity and power consumption of the compressor due to the increase in the number of compressors is automatically suppressed.

Driving capacity (consumption capacity), volumetric efficiency, and cooling performance when used in a cooler for a gas compressor to which this invention is applied and a conventional gas compressor (the opening degree of the intake path is constant) to which this invention is not applied. Figure 4 shows the characteristics of capacity (work ability) versus rotational speed. In the same figure, the solid line is the conventional one, the broken line is
The characteristics shown in (b) and (c) are for the gas compressor of the present invention. Characteristics A, B, and C are for the above spring 19.
These are the characteristics of three gas compressors with different spring forces and different minimum intake openings. B is the characteristic when the minimum intake opening is made smaller than A, and C is the characteristic when the spring force is made weaker. In this way, various characteristics can be obtained by appropriately selecting the minimum intake opening degree and spring force. As is clear from this figure, according to the gas compressor of the present invention, as the rotation speed increases, the volumetric efficiency decreases, and increases in work capacity and power consumption are suppressed.

As explained in detail above, in the gas compressor according to the present invention, by simply providing a simple spool valve on the cylinder, it is possible to suppress increases in work capacity and power consumption in the high rotation speed region. This makes it suitable as a gas compressor for car coolers.

[Brief explanation of the drawing]

Figures 1 and 2 are a front sectional view and a side sectional view of a gas compressor according to an embodiment of this invention, Figures 3a and b are sectional views taken along the - line in Figure 2, and Figure 4 is a sectional view of a gas compressor according to an embodiment of this invention. It is a characteristic diagram showing the effect. 4... Cylinder, 8... Vane, 9... Rotor, 12... Distribution hole, 12a... Circular hole, 12
b...Oval hole, 13...Intake port, 18...
...Spool, 19...Spring.

Claims (1)

[Scope of Claim for Utility Model Registration] A gas compressor that has a rotor and vanes that are slidable in the radial direction of the rotor in a cylinder chamber, an intake port for introducing gas into the gas compressor, and an intake port that connects the inside and outside of the cylinder chamber. A circulation hole is formed in the cylinder that communicates with the intake port passing through the cylinder, and a spool is mounted inside the circulation hole with one end facing the intake port and biased toward the intake port by a spring, so that the above-mentioned flow from the intake port is attached. The gas sucked into the cylinder chamber through the hole and the intake port is received at one end of the spool, and a throttle valve mechanism is configured such that the opening degree of the intake port becomes smaller as the flow velocity of the gas increases. gas compressor.