JPH0355836Y2 - - Google Patents

Description

[Detailed Description of the Invention] <<Industrial Application Field>> This invention relates to a variable capacity gas compressor used in car coolers, etc., and particularly relates to a gas compressor with improved cooling capacity during the initial stage of operation.

[Prior art and its problems] Gas compressors used for air conditioning in passenger cars are usually installed in parallel with the engine, driven by a V-belt from the engine's crankshaft pulley, and driven by an electromagnetic clutch attached to the compressor. I try to connect it with the side.

Therefore, the capacity of this type of gas compressor increases in proportion to the rotational speed of the engine, but this also means that when driving at high speed, the gas compressor is driven at high speed, so This has the disadvantage of causing the vehicle interior to become overcooled and increasing the power consumption in proportion to this, and this tendency is particularly noticeable in rotary gas compressors (see Figure 6). The dotted line in the middle of the graph indicates the cooling capacity of this type of gas compressor).

Therefore, the applicant has previously proposed various so-called variable capacity type gas compressors that vary the capacity of a refrigerant gas compression chamber in accordance with the driving speed of the gas compressor.

For example, by providing a control plate on the inner surface of the front side block of a compressor, providing a concave portion in the control plate that serves as an inlet that communicates the communication hole of the front side block with the cylinder chamber, and rotating the control plate by a predetermined angle. A typical example is one in which the intake capacity of the air taken in through the communication hole in the front side block is variable.

However, in this type of variable capacity gas compressor, the suction pressure is always kept constant, and
Although it is configured to maintain the set temperature, it takes nearly twice as long to reach the set temperature as compared to a conventional gas compressor (as shown by the dashed line in FIG. 6).

For this reason, this type of variable capacity gas compressor has not been able to meet the demands of rapidly cooling the interior of a vehicle when the interior temperature of the vehicle is quite high, especially during the day in the summer.

Therefore, the inventors decided to have the function of a conventional gas compressor, which is not a variable capacity type, in the initial stage of operation, that is, until the set temperature is reached, and then to have the function of a variable capacity type gas compressor after reaching the set temperature. He realized that by doing so, he could obtain a truly ideal gas compressor, and completed this idea.

《Purpose of the invention》 This invention was made based on the points mentioned above, and its purpose is to keep the capacity of the compression work chamber constant during the initial stage of operation, to enable rapid cooling, and to maintain the temperature at the set temperature. Once achieved, the objective is to provide an extremely practical gas compressor that functions as a variable capacity gas compressor, prevents overcooling, and reduces power consumption.

<<Structure of the invention>> In order to achieve the above object, the present invention includes a cylinder whose inner circumference is formed into a substantially elliptical shape, front and rear side blocks attached to both sides of this cylinder, and the cylinder and both side blocks. a rotor that is rotatably suspended horizontally in a cylinder chamber and has a plurality of vanes that can move forward and backward in the radial direction; and a control plate that is rotatably mounted on the inner surface of the front side block within a predetermined angle. and a control plate driving means for driving the control plate, which rotates the control plate according to the suction pressure in the suction chamber and communicates the communication hole formed in the front side block with the cylinder chamber. In a gas compressor in which the capacity of the compression work chamber is variable according to the operating state by continuously moving the suction port of the gas compressor, the control plate driving means connects the front end to the control plate while the rear end is connected to the control plate. A cylinder is arranged to move forward and backward in the suction chamber with the external view, a spring is inserted into the cylinder and biases the cylinder toward the suction chamber with a predetermined spring pressure, and a spring is inserted into the cylinder to bias the cylinder toward the suction chamber. A cylinder locking means for stopping the forward and backward movement of the cylinder, and a lock releasing means for releasing the cylinder lock when the temperature inside the vehicle is below a set temperature, and the cylinder locking means is provided until the temperature inside the vehicle reaches the set temperature. When the cylinder is locked and the control plate is in an immovable state, and the temperature inside the vehicle reaches the set temperature, the lock release means is activated to release the lock on the cylinder and reduce the intake pressure and spring pressure in the suction chamber. The cylinder is moved forward and backward by the differential pressure between the cylinder and the control plate, and the control plate is rotated by a desired angle as the cylinder moves forward and backward.

<<Description of Embodiments>> Hereinafter, preferred embodiments of the present invention will be described in detail using the drawings.

FIG. 1 is a longitudinal cross-sectional view of a gas compressor according to the present invention;
Fig. 2 is a cross-sectional view of the gas compressor, Fig. 3 is a longitudinal sectional view showing the driving means of the control plate used in the gas compressor, and Figs. 4 and 5 show high-speed and low-speed operation. A vertical cross-sectional view of a gas compressor shown respectively,
FIG. 6 and FIG. 7 are graphs showing the correlation between the operating time of the gas compressor and the cooling temperature.

In FIG. 1, this gas compressor includes a compressor main body 1, a casing 2 with an open end that hermetically surrounds the main body 1, and a front head 3 attached to the open end surface of the casing 2.

The compressor main body 1 has a cylinder 4 having a substantially elliptical inner circumference, and a front side block 5 and a rear side block 6 attached to both sides of the cylinder 4. In the cylinder chamber of the rotor shaft 7, there are five vanes 8 which are integral with the rotor shaft 7 and can freely move forward and backward in the radial direction around the rotor shaft 7.
A solid cylindrical rotor 9 equipped with a rotor 9 is horizontally suspended so as to be freely rotatable.

Further, a substantially disk-shaped control plate 10 is pivotally attached to the inner surface of the front side block 5, and this control plate 10 is rotatable within a predetermined angle.

A recess (intake port) 11 is formed in the peripheral edge of the control plate 10, and the communication hole 12 of the front side block 5 and the cylinder chamber 13 communicate with each other through the recess 11.

In other words, during high-speed operation, the suction pressure decreases, so the control plate 10 is rotated, and the concave portion 11 moves accordingly, and the capacity of the compression work chamber becomes small and attempts to increase the suction pressure.

On the other hand, during low-speed operation, the suction pressure increases, so the control plate 10 rotates in the opposite direction to the above, and the concave portion 11 moves thereby, so that the capacity of the compression work chamber becomes the maximum capacity.

Note that the driving means for this control plate 10 will be described later.

When the rotor 9 is driven to rotate, the low-pressure refrigerant gas introduced from the intake hole 14 provided in the front head 3 is 180 degrees opposed to the front side block 5, as shown by the solid arrow in FIG. The high-pressure gas is sucked into the cylinder chamber 13 through the communication hole 12 formed in the cylinder chamber 13, and then the high-pressure gas compressed within the cylinder chamber 13 passes through the discharge port 15 and the discharge valve 16 to the gap between the cylinder 4 and the inner periphery of the casing 2. The oil is discharged to the oil separator 1 at the back of the block 6 through a communication hole 17 provided in the rear side block 6 with a phase difference of approximately 90° from the communication hole 12.
8 and is discharged to the outside from the rear space of the casing 2 through the discharge port 19 as shown by the broken line arrow in FIG.

Next, the main part of this invention, that is, the control plate 1
The driving means of 0 will be explained.

That is, in a suction chamber 20 formed between the front side block 5 and the front casing 3, a cylinder 21 is disposed in a direction perpendicular to the axis of the compressor. The tip 21a of this cylinder 21 faces into the suction chamber 20, and the other end 21a faces into the suction chamber 20.
1b faces the outside.

Further, a spring 22 is inserted into the cylinder 21, and the spring 22 has an appropriate spring pressure so as to always urge the cylinder 21 toward the suction chamber 20 side.

On the other hand, a drive pin 23 is provided upright on the surface of the control plate 10, and this pin 23 passes through a cam groove 24 formed in an arcuate shape in the front side block 5.
The tip 23a faces the suction chamber 20 side. This tip 23a is fitted into an engagement recess 25 provided at the tip of the cylinder 21, and as the drive pin 23 moves within the cam groove 24 as the cylinder 21 operates, the control plate 10 is rotated by a predetermined angle. It is designed to be driven freely.

Furthermore, in the present invention, cylinder locking means for locking the cylinder 21 under predetermined conditions and lock release means for unlocking the cylinder are provided.

The cylinder lock means and lock release means in this embodiment will be explained. That is, a locking hole 27 is provided in the side surface of the cylinder 21, and a spool 29 biased by a spring 28 is configured to engage with the locking hole 27. Since this spool 29 is normally engaged in the locking hole 27, the cylinder 21 is reliably locked. Therefore, cylinder 21
When the control plate 10 is locked, the control plate 10
remains fixed and the capacity of the compression chamber is always at its maximum.

Next, in order to release the lock of this cylinder 21, solenoid coils 30, 30 are set on both sides of the spool 29 in this embodiment, and when the solenoid coil 30 is energized, an electromagnetic attraction force acts, and the spool 29 is pulled into a spring state. The cylinder 21 is sucked in the direction of the arrow against the spring force 28, and the engagement between the spool 29 and the locking hole 27 is released, and the cylinder 21 becomes able to move forward and backward.

The timing for energizing the solenoid coil 30 may be such that the solenoid coil 30 is energized when the temperature inside the vehicle reaches a predetermined temperature based on a temperature sensor (not shown) set in the vehicle interior. Alternatively, the solenoid coil 30 may be energized by a signal from a sensor that detects the temperature of air blown from an evaporator (not shown).

In short, a sensor installed in the vehicle interior or near the evaporator detects the ambient temperature, and the cylinder locking means locks the cylinder 21 until the preset temperature is reached, and rapid cooling is performed. When this is reached, the solenoid coil 30 is energized, the locking means of the cylinder is released, and the cylinder 21 is in a state where it can move forward and backward.

When the cylinder 21 becomes able to move forward and backward, the cylinder 21 moves forward and backward due to the differential pressure between the spring pressure of the spring 22 and the suction pressure in the suction chamber 20. As the cylinder 21 advances and retreats, the control plate 10 rotates around the axis by a predetermined angle, and the concave portion (suction port) 11 moves continuously, making the capacity of the refrigerant gas compression chamber variable and constantly performing compression work. The suction pressure taken into the room is set at a constant value (approximately 2 kg/
cm ² is preferred).

FIG. 4 shows the positional relationship of the control plates 10 during high-speed operation, and FIG. 5 shows the positional relationship of the control plates 10 during low-speed operation.

Further, the graph in FIG. 7 shows the cooling capacity of the gas compressor of the present invention.

<Configuration and Effects of the Invention> As explained above, the gas compressor according to the present invention is compatible with both conventional gas compressors (types in which the capacity of the compression work chamber cannot be varied) and variable capacity gas compressors. By incorporating only the advantages of the conventional gas compressor and providing a cylinder locking means that stops the drive of the control plate at the beginning of operation, rapid cooling is possible by taking advantage of the advantages of conventional gas compressors, and after reaching the set temperature, By releasing the cylinder locking means and rotating the control plate, the capacity of the compression chamber is controlled, preventing overcooling and significantly reducing power consumption. This is an extremely practical idea, as it can rapidly cool the inside of a car, especially during summer days, achieve a comfortable temperature in a short time, maintain this comfortable temperature for a long period of time, and save on fuel consumption.

[Brief explanation of drawings]

Fig. 1 is a vertical cross-sectional view showing the overall structure of the gas compressor according to the present invention, Fig. 2 is a cross-sectional view of the gas compressor, and Fig. 3 is the main part of the gas compressor, that is, the drive of the control plate. Fig. 4 is a longitudinal sectional view of the gas compressor during high-speed operation, Fig. 5 is a longitudinal sectional view of the gas compressor during low-speed operation, and Fig. 6 shows the cooling capacity of a conventional compressor. The graph shown in FIG. 7 is a graph showing the cooling capacity of the gas compressor according to the present invention. 4...Cylinder, 5...Front side block, 6...Rear side block, 9...Rotor,
10...control plate, 11...recess (intake port),
13...Cylinder chamber, 14...Intake port, 20...
Suction chamber, 21... cylinder, 22... spring, 23... drive pin, 24... cam groove, 25...
...Engagement recess, 27...Latching hole, 28...Spring, 2
9...Spool, 30...Solenoid coil.

Claims (1)

[Claims for Utility Model Registration] A cylinder whose inner periphery is approximately elliptical, front and rear side blocks attached to both sides of the cylinder, and a rotating cylinder inside the cylinder chamber constituted by the cylinder and both side blocks. A rotor that is freely suspended horizontally and has a plurality of vanes that can move forward and backward in the radial direction, a control plate that is rotatably mounted on the inner surface of the front side block within a predetermined angle, and drives this control plate. and a control plate driving means that rotates the control plate according to the suction pressure in the suction chamber to continuously drive the suction port of the control plate that communicates the communication hole formed in the front side block with the cylinder chamber. In a gas compressor in which the capacity of the compression work chamber is made variable according to the operating state by moving the control plate, the control plate drive means has a front end connected to the control plate, and a rear end facing outside to drive the suction chamber. a cylinder that is arranged to move forward and backward; a spring that is inserted into the cylinder and biases the cylinder toward the suction chamber with a predetermined spring pressure; and a cylinder that fixes the cylinder and stops the forward and backward movement of the cylinder. and a lock release means for releasing the cylinder lock when the vehicle interior temperature is below a set temperature, and the cylinder is locked by the cylinder lock means until the vehicle interior temperature reaches the set temperature. When the control plate is in a non-moving state and the temperature inside the vehicle reaches the set temperature, the lock release means is activated to release the lock on the cylinder and release the cylinder due to the differential pressure between the intake pressure in the suction chamber and the spring pressure. A gas compressor characterized in that the cylinder is moved forward and backward, and a control plate is rotated by a desired angle as the cylinder moves forward and backward.