JP2678455B2 - Gas compressor - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a gas compressor, and more particularly to a rotary vane type variable capacity gas compressor used in a car cooler or other relatively small refrigerating apparatuses.

<< Summary of the Invention >> The present invention reduces the pressure to low when the rotor rotates at high speed, while
The hydraulic pressure of the control plate drive mechanism that is maintained at a high pressure during constant speed rotation is supplied to the vane pressure chamber to obtain the vane pressure.

<Prior Art> A conventional rotary vane type variable capacity gas compressor has a solid cylindrical rotor equipped with a plurality of vanes that can move back and forth in a radial direction inside a cylinder chamber with a substantially elliptical cylindrical inner circumference. It is laid free to rotate.

A compression work chamber is formed in a crescent-shaped space surrounded by the cylinder inner wall and the solid cylinder outer peripheral wall, and when the vane moves in this compression work chamber, while sucking gas (refrigerant gas) into the compression work chamber, The previous vane acts to compress the sucked gas in the subsequent vane.

At this time, a vane pressure is applied to the vane so as to contact the inner wall of the cylinder at a predetermined pressure in order to prevent a chattering phenomenon at the time of compression work, and this pressure uses the hydraulic pressure generated by the discharge gas pressure.

By the way, in a variable displacement compressor, a rotatable control plate is arranged on the end face of a rotor, and a gas compressed by a vane is bypassed by partially bypassing the gas sucked through the control plate. It is configured so that the capacity of can be adjusted.

This type of gas compressor is effective when used for a car cooler. That is, since the gas compressor is driven to rotate via the engine shaft and the V-belt, there is a possibility that the engine will be overcooled as the engine speed increases. This is because it is possible to prevent the supercooling by controlling the amount of gas compressed when it becomes low.

<< Problems to be Solved by the Invention >> However, in the above gas compressor, since the vane pressure is constantly kept high by the hydraulic pressure generated by the discharge gas pressure, the friction torque at the tip of the vane is large and the driving power is large. There was a drawback that

In particular, when the amount of compressed gas is adjusted to a low level during high-speed operation, the vane pressure is kept high even when the vane tip is not compressed until it passes through the bypass hole. there were.

Further, when the friction torque increases, the amount of friction heat increases, which not only raises the temperature of the discharge gas, but also increases the wear of the vanes.

<< Means for Solving the Problems >> The present invention has been made to solve the above problems, and includes an inner peripheral substantially elliptic cylinder cylinder block provided between a pair of side blocks, and A rotor rotatably mounted horizontally in a cylinder chamber formed by the cylinder block and the both side blocks, a vane mounted in a vane groove provided in the rotor so as to move back and forth, the rotor and the one side block. After having a control plate rotatably provided between the control plate and a control plate drive mechanism for rotationally driving the control plate, the volume of gas sucked from the intake side is adjusted by the control plate and compressed in the cylinder chamber. In the rotary vane type gas compressor for discharging, one end of the control plate drive mechanism abuts a spring and the control plate drive mechanism Connected and located on the intake side and pressed by the pressure and spring pressure on the intake side, the other is located in the chamber to which the hydraulic pressure of the lubricating oil generated by the discharge gas pressure is supplied and is pressed by the hydraulic pressure, A drive shaft that stops moving at a position where the two pressing forces are balanced, and a discharge path that connects the chamber and the intake side are provided, and when the rotor rotates at high speed, the hydraulic pressure in the chamber is reduced and compressed. A hydraulic pressure release valve that moves the drive shaft so as to reduce the amount of gas to be discharged, and a communication passage that communicates the chamber with the vane groove, and the control plate is rotationally driven by the movement of the drive shaft, The capacity of the compression working chamber in the cylinder chamber is changed by the rotational position of the control plate, and the hydraulic pressure in the chamber is applied to the bottom of the vane groove via the communication passage. .

<< Operation >> According to the present invention, the hydraulic pressure for driving the control plate having the above-described structure decreases as the rotation speed increases, and the control plate is rotated so as to reduce the amount of compressed gas, and the vane pressure is generated by the hydraulic pressure. Therefore, the vane pressure acts so as to decrease as the hydraulic pressure decreases.

<< Description of Examples >> Hereinafter, one example of a gas compressor according to the present invention will be described with reference to the accompanying drawings. The basic configuration of the gas compressor in this embodiment was previously proposed by the applicant in Japanese Patent Application No. 62-3003.

FIG. 1 is a vertical sectional view of a gas compressor body according to the present invention,
2 is a sectional view taken along the line II-II in FIG. 1 and FIG. 3 is a sectional view taken along the line III-III in FIG. 1. The gas compressor body 1 is a casing 2 of one-end opening type, and this casing 2 The front head 3 is provided on the opening end face of the.

Inside the casing 2, there is provided a pair of side blocks including a cylinder block 4 having a substantially elliptic cylinder shape on the inner circumference, and a front side block 5 and a rear side block 6 mounted on both sides of the cylinder block 4, and formed by these. A solid cylindrical rotor in which an inner peripheral substantially elliptic cylinder-shaped cylinder chamber a is integrated with the rotor shaft 7 and is equipped with five flat plate-shaped vanes 8 which can move forward and backward in the radial direction. 9 is horizontally rotatably mounted.

The vane 8 is attached to the rotor 9 around the rotor 9,
A vane groove 9a extending in the rotation axis direction and having a cross section slightly larger than the cross section of the vane 8 and having a depth slightly deeper than the height of the vane 8 is provided, and the vane 8 is inserted into the vane groove 9a. Has been done.

At the bottom of the vane groove 9a, a vane pressure chamber 9b having a larger cross-sectional area than the upper portion is formed.
The lubricating oil O in the casing 2 is supplied to the.

That is, the lubricating oil O communicates with the oil distribution paths 6a, 4a, 5a formed in the rear side block 6, the cylinder block 4 and the front side block 5, the control plate drive mechanism described later, and the control plate drive mechanism and the vane groove 9a. Is supplied to the vane pressure chamber 9b through the communication passage.

Between the front side block 5 and the cylinder block 4, a substantially disc-shaped control plate 10 is fitted on and supported by the rotor shaft 7.

Bypass recesses 11, 11 are provided at the periphery of the control plate 10.
The bypass recesses 11 are provided facing each other by 80 °.
Are configured to communicate with the suction port 12 and the bypass hole 5b provided in the front side block 5.

That is, the control plate 10 can be rotated within a predetermined angle by a control plate drive mechanism described later. For example, when the rotor 9 rotates at a constant speed, the control plate 10 rotates to a position where the sucked refrigerant gas is not bypassed. However, the capacity of the compression working chamber in the cylinder chamber a is secured to the maximum.

On the other hand, during high-speed operation, the control plate is adjusted according to the high speed.
The reference numeral 10 rotates clockwise in FIG.
And the bypass hole 5b provided in the side block 5 communicate with each other, a part of the refrigerant gas in the compression work chamber is bypassed to the suction side through the bypass hole 5b, and as a result, the capacity of the compression work chamber is reduced, which reduces Compressed in minutes only.

Before describing the control plate drive mechanism, the flow of the refrigerant gas in the variable capacity gas compressor configured as described above will be described.

First, the refrigerant gas introduced from the intake port 14 provided in the front head 3 into the intake chamber 15 passes through the intake port 12 and the intake gas penetratingly formed in the cylinder block 4 as shown by an arrow A in FIG. It is introduced into the passage 16 and is sucked into the cylinder chamber a through the notches 17a and 17b provided at both ends of the intake passage 16.

Next, the high-pressure gas compressed by the rotation of the vane 8 is supplied to the oil separator 19 provided at the back of the rear side block 6 through the discharge port 18a, the discharge valve 18b, the communication hole 6b provided at the rear side block 6, As shown by arrow B in FIG. 1, it reaches the rear space b of the casing 2 and is discharged to the outside through the discharge port 20.

Further, since the lubricating oil O in the rear space b is maintained at a high pressure (15 to 20 kg / cm ² ) by the compressed high pressure gas, the oil formed in the cylinder block 4, the front side block 5 and the rear side block 6 is The lubricating action is supplied to the shaft of the rotor 9 through the flow paths 4a, 5a and 6a, and the vane pressure is generated by being supplied into the vane compression chamber 9b as described above.

The drive mechanism 30 for the control plate 10 is shown in FIG. That is, a long hole 31 having a two-step diameter reaching from the outer peripheral end of the front head 3 to the inner wall of the suction chamber 15 facing the one end is recessed, and the short diameter portion 31a in the long hole 31 is hermetically sealed,
The drive shaft 33 is slidably housed, and the spring 32 is in contact with the tip of the drive shaft 33. The tip of the large diameter portion 31b is sealed with a stopper 34 to form a chamber 31c.

A concave portion 34 is formed at the tip of the drive shaft 33 on the spring 32 side, and a pin 35 integrally provided with the control plate 10 penetrates through the guide hole 36 formed in the front side block 5 in the concave portion 34. And is being fitted loosely. Therefore, when the drive shaft 33 moves in the long hole 31, the control plate 10 is rotated accordingly.

In the chamber 31c provided on the large diameter portion 31b side of the long hole 31, an oil distribution path 5a communicating with the oil distribution path 4a provided in the cylinder block 4 and a mechanical seal chamber 7a of the rotor shaft 7 are provided.
A communication hole 37 that communicates with and a discharge passage 39 that communicates with the intake side with a hydraulic pressure discharge valve composed of a solenoid valve 38 interposed therebetween is opened.

The mechanical seal chamber 7a includes the front side block 5
A passage 40 is provided in the control plate 10, which communicates with the groove 22 of the control plate 10. That is, the groove 22, the passage 40, the mechanical seal chamber 7a, and the communication hole 37 constitute a communication passage that communicates the chamber 31c with the vane groove 9a.
Therefore, the vane pressure chambers 9b, 9b ... Provided at the bottom of the vane grooves 9a, 9a ... And the discharge side are maintained in communication with each other through the oil flow passages 6a, 4a, 5a and this communication passage. It

The solenoid valve 38 is controlled by the engine speed and the rotor 9 speed.

That is, the number of rotations is above a certain level (for example, 4000 rpm or more)
When the solenoid valve 38 is turned on, the rod 38a is projected and the ball 38b is pushed out, the discharge passage 39 is opened, and a part of the hydraulic pressure in the chamber 31c is discharged to the intake side through the discharge passage 39,
The oil pressure in the chamber 31c decreases by the amount of the discharge.

Therefore, the pressure on the intake side, that is, one of the pressure of the suction chamber 15 (1.5 to 2.0 Kg / cm ² ) and the repulsive force (spring pressure) of the spring 32, and the hydraulic pressure (15
The drive shaft 33, which was stopped by being balanced by the other pressure of ²⁰ Kg / cm ² ), moves to the chamber 31c side by the amount of the decrease in the pressure in the chamber 31c, and causes the control plate 10 to release the refrigerant gas. Rotate to bypass.

At this time, the reduced hydraulic pressure in the chamber 31c is applied to the vane pressure chamber 9b via the communication hole 37, the mechanical seal chamber 7a, the communication passage formed by the passage 40 and the groove 22, so that the vane pressure becomes low. Therefore, the friction torque can be reduced, the driving power can be reduced, the frictional heat generation can be reduced, and the discharge gas temperature can be lowered.

On the other hand, when the rotation speed of the rotor 9 or the engine is low and the solenoid valve 38 is off, the lot 38a moves backward and the ball 38b
Closes discharge path 39. Therefore, since the hydraulic pressure in the chamber 31c is not released and the pressure increases, the pressure moves on the both sides against the repulsive force of the spring 32 until the pressures on both sides are balanced, and the control plate 10 is rotated in the opposite direction from the above high-speed rotation. Rotate to.

At this time, the high-pressure oil pressure in the chamber 31c is applied to the vane pressure chamber 9b via the communication passage, so that the vane pressure is increased and the chattering phenomenon is effectively prevented.

<< Effects >> As described above, in the gas compressor according to the present invention,
Since the vane pressure is obtained by the hydraulic pressure of the control plate drive mechanism which is kept low when the rotation speed of the rotor is high and is kept high when the rotation speed is low, the friction torque at the time of high speed rotation can be reduced.

Therefore, the driving power can be small, so that the fuel consumption can be improved, the frictional heat can be reduced, and the discharge gas temperature can be lowered, so that the cooling effect can be enhanced.

BRIEF DESCRIPTION OF THE DRAWINGS The drawings show one embodiment of the gas compressor according to the present invention, wherein FIG. 1 is a longitudinal sectional view thereof, and FIG. 2 is II- of FIG.
A sectional view taken along line II and FIG. 3 are sectional views taken along line III-III in FIG. 1 ... Gas compressor body 2 ... Casing 3 ... Front head 4 ... Cylinder block 5 ... Front side block 6 ... Rear side block 8 ... Vane 9 ... Rotor 9a ... Vane groove 9b ... Vane pressure Chamber 10 …… Control plate 15 …… Suction chamber (intake side) 30 …… Control plate drive mechanism 31c …… Room 32 …… Spring 33 …… Drive shaft 37 …… Communication hole 38 …… Solenoid valve 39 …… Discharge path a: Cylinder chamber

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Naoki Kazeno 4-3-1 Yashiki, Narashino City, Chiba Prefecture Seiko Seiki Co., Ltd. (56) References JP 62-251488 (JP, A) Sho 62-200190 (JP, U)

Claims (1)

(57) [Claims] 1. A cylinder block, which is provided between a pair of side blocks and has a substantially elliptic cylindrical shape on the inner circumference, and a rotor rotatably laterally installed in a cylinder chamber formed by the cylinder block and the side blocks. A vane movably mounted in a vane groove provided in the rotor, a control plate rotatably provided between the rotor and the one side block, and a control plate drive for rotationally driving the control plate. A rotary vane type gas compressor having a mechanism for adjusting the capacity of a gas sucked from the intake side by a control plate, compressing the gas in a cylinder chamber, and then discharging the gas. One end of the control plate drive mechanism abuts a spring. Together with the control plate, is located on the intake side and is pressed by the pressure on the intake side and the spring pressure. On the other hand, the other is a drive shaft that is located in a chamber to which the hydraulic pressure of the lubricating oil generated by the discharge gas pressure is supplied, is pressed by the hydraulic pressure, and stops moving to a position where the balance of both pressing forces is maintained, A hydraulic pressure release valve that is provided in a discharge path that communicates the interior and the intake side, and that moves the drive shaft so as to reduce the amount of gas compressed by reducing the hydraulic pressure in the interior when the rotor rotates at high speed; And a communication passage that communicates the interior of the chamber with the vane groove, the control plate is rotationally driven by the movement of the drive shaft, and the capacity of the compression working chamber in the cylinder chamber is changed by the rotational position of the control plate. A gas compressor, wherein hydraulic pressure in the chamber is applied to the bottom portion of the vane groove via the communication passage.