JPS6237239B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a vane rotary compressor used, for example, in an automobile air conditioner, and further relates to a method for supplying lubricating oil that presses the bottom of the vane and lubricates both sides of the rotor. This relates to a stopping device.

BACKGROUND ART A conventional rotary compressor of this type is disclosed in, for example, Japanese Unexamined Patent Publication No. 133811/1983.
This rotary compressor is provided with an oil passage opening/closing member that rotates synchronously with the rotor at the end of the rotor shaft.
That is, this oil passage opening/closing member has a plurality of openings on the same diameter, and while the rotor is rotating, lubricating oil is supplied to the end surface of the rotor through these openings, and
When the rotor stops rotating, this oil passage opening/closing member also stops, blocking the oil passage and preventing oil from flowing into the cylinder.

Problems to be Solved by the Invention However, with the above configuration, the oil passage is not necessarily blocked when the rotor stops, and if the rotor stops with the opening communicating with the oil passage, oil will flow into the cylinder. It gets crowded.

Since refrigerant gas is dissolved in the oil that has flowed into the cylinder, it evaporates and expands in the low-pressure cylinder. Therefore, the rotor rotates in reverse for a short time, and the next opening provided in the oil passage opening/closing member communicates with the oil passage. This phenomenon is repeated several times, causing the rotor to rotate in reverse for several seconds even after the rotor has stopped, resulting in an increase in the amount of oil that accumulates in the cylinder, causing problems when the cylinder is restarted. Was.

Therefore, the present invention provides a vane rotary compressor that supplies lubricating oil to the bottom of the vane and the end surface of the rotor.
The purpose is to reliably stop the supply of lubricating oil in response to the stoppage of rotation of the rotor.

Means for Solving the Problem Therefore, the vane rotary compressor of the present invention includes a cylinder having the same cylindrical shape having a discharge port and a refrigerant suction port, both ends of which are closed by a front side wall and a rear side wall, and a cylinder inside the cylinder. A rotor that is eccentrically arranged and rotatable, a plurality of vane grooves formed in the rotor, and a plurality of vane grooves that are provided in each of these vane grooves so as to be able to protrude and retract, the tip of which is in contact with the inner surface of the cylinder, and the inside of the cylinder is connected to the discharge port. a vane that partitions the compression space into a compression space that communicates with the refrigerant suction port and the suction space that communicates with the refrigerant suction port; a discharge valve that is provided at the discharge port and opens when the pressure in the compression space reaches a predetermined value or more; an oil separation chamber that covers an outlet and the rear side wall and has a refrigerant outlet; an annular circumferential groove provided on the inner surface of the rotor side of the rear side wall and located on the rotation locus of the bottom of the vane groove; and a valve storage hole provided in the oil separation chamber and the oil passage, a valve body is slidably provided in the valve housing hole, and one end of the valve body in the sliding direction of the valve body in the storage hole is provided. The valve body is in communication with the compression space and the other end is in communication with the oil separation chamber, and the valve body blocks the oil passage when it is located at one end of the storage hole, and when it is located at the other end. The oil passage is configured to communicate with the oil passage when the oil passage is in use.

Effect With the above configuration, when the rotor rotates, the pressure on the compression space side communicating with the discharge port in front of the discharge valve is higher than the pressure on the oil separation chamber side, so the pressure applied to one end of the valve element is lower than the pressure applied to the other end. The valve body becomes larger and slides to a position where it communicates with the oil passage, and lubricating oil is supplied to the bottom of the vane and the end face of the rotor. When the rotor stops rotating, the rotor rotates slightly in reverse because at the moment of the stop, there is a pressure difference in the cylinder between the compression space communicating with the discharge port and the suction space communicating with the refrigerant suction port. Therefore, as the volume of the compression space increases due to this reversal, the pressure on the side of the compression space closed by the discharge valve rapidly decreases, and becomes lower than the pressure on the side of the oil separation chamber. As a result, the pressure applied to the other end of the valve element becomes greater than the pressure applied to one end, and the valve element slides to a position where it communicates with the oil passage, stopping the supply of lubricating oil.

Embodiment An embodiment of the present invention will be described below based on the drawings.

Figure 1 is a sectional view taken along the direction perpendicular to the rotor axis, including the rotor of a vane rotary compressor, Figure 2 is a sectional view taken along line AA in Figure 1, and Figures 3 and 4 are valves that open and close oil passages. The operating conditions of the mechanism are shown, with FIG. 3 showing the state when the compressor is stopped, and FIG. 4 showing the state when the compressor is rotating.

In the figure, 1 is a rotor, which is provided in a cylinder 2 so as to be rotatable around an eccentric position.
3 is a front side wall that covers the front opening of the cylinder 2.
4 is a rear side wall that covers the rear opening of the cylinder 2.
5 is a vane slidably fitted into a vane groove 16 formed in the rotor 1; 6 is a refrigerant suction port formed in the cylinder 2; 7 is a refrigerant discharge port.
8 is a discharge valve provided opposite to the refrigerant discharge port 7; 9 is a cylinder head provided to cover the discharge valve 8; 1;
0 is a discharge chamber 11 formed by the cylinder head 9
This is a cover that forms the oil separation chamber 12 so as to communicate with the oil separation chamber 12. 13 is a high-pressure refrigerant outlet formed in a part of the cover 10. 14 is a bearing that supports the rotor 1, 15 is a shaft sealing device, and the above constitutes a vane rotary compressor.

Reference numeral 17 denotes a circumferential groove for supplying high-pressure lubricating oil to the bottom of the vane groove 16, and is provided on the rear side wall 4.

Reference numeral 18 denotes a take-out passage for the front pressure of the discharge valve 8, which is provided in the cylinder 2. 19 and 20 are passages that transmit the pressure of the respective outlet passages 18; 21 is an oil passage that sends lubricating oil to the circumferential groove 17, and is located downstream of the valve mechanism;
2 is an oil passage located upstream of the valve mechanism, and the other end thereof is opened below the surface of the lubricating oil 23 in the oil separation chamber 12. To explain the structure of the valve mechanism, 2
4 is a valve body, 25 is a circumferential semicircular groove provided in the valve body 24, 26 is a return spring, and 27 is a set screw for the spring, which has a small hole 28 in the center of the screw. 29 is a valve housing hole in which the valve body 24 is housed.

Note that a refrigeration cycle described below is connected to the refrigerant outlet 13 and refrigerant inlet 6 of the compressor.
A discharge pipe (not shown) is generally connected to the refrigerant outlet 13, and the gaseous refrigerant, which is pressurized by a compressor and has a high temperature and high pressure, is guided to a condenser (not shown).

A condenser plays the role of changing high-temperature, high-pressure gaseous refrigerant into high-pressure liquefied refrigerant by cooling it. Usually, air is blown onto the outside surface of the condenser using a fan to cool it and cause the refrigerant to condense and liquefy. It is something to be done.

This high pressure liquefied refrigerant is then led from the condenser through a liquid refrigerant pipe (not shown) to a pressure reduction mechanism, ie, a throttle valve, commonly referred to as an expansion valve. The liquid refrigerant passes through the expansion valve and is guided to the evaporator (inlet) by a low-pressure liquid pipe. The other end (outlet) of the evaporator is connected to the refrigerant suction port 6 of the compressor via a suction gas pipe (not shown), and the evaporator is always kept at a low pressure while the compressor is rotating. Therefore, the liquid refrigerant that has passed through the throttle valve is rapidly evaporated inside the evaporator. In this way, by absorbing the heat of vaporization from outside the evaporator, cooling power and cooling power can be obtained.

Next, the effect will be explained.

When the rotor starts to rotate in the direction of the arrow shown in FIG. , oil separation chamber 12
The lubricating oil in the refrigerant is separated therefrom and the refrigerant is discharged via the outlet 13.

Focusing on the pressure across the discharge valve 8 in the flow of refrigerant as described above, the pressure at the refrigerant discharge port 7 before the discharge valve, that is, the pressure in the passage 20, and the pressure after passing through the discharge valve, that is, the pressure in the space of the spring 26 are as follows. While the compressor is rotating, the pressure inside the passage 20 becomes higher. Valve body 24
There is a difference in the force received by both end faces of the valve body 24, and the spring force is set so that the valve body 24 moves downward in the figure against the force of the spring 26. Therefore, the downward movement of the valve body 24 causes
As shown in Figure 4, oil passage 22 → semicircular groove 25 → oil passage 21 →
The circumferential groove 17 is communicated, and the vane 5 is brought into close contact with the cylinder.

Next, when the compressor stops rotating, the discharge valve 8 immediately closes. As a result, the pressure on the outlet 13 side becomes the same as the pressure on the oil separation chamber 12 because it is connected to the high pressure side of the refrigerant cycle as is well known. The pressure on the outlet 13 side is reduced through a pressure reducer (not shown) in an attempt to balance with the low pressure side of the refrigeration cycle, but the speed at which this equilibrium is achieved is slow and the pressure within the refrigerant discharge port 7 is reduced quickly. That is, due to gas leakage from gaps such as the gap between the rotor 1 and the front and rear side walls 3 and 4, the gap between the vane 5 and the cylinder 2 or the front and rear side walls 3 and 4, and the top gap between the rotor 1 and the cylinder 2, as well as the pressure difference within the cylinder. Due to a slight rotation of the rotor, etc., the pressure inside the discharge port 7 quickly drops. Due to this, the pressure in the passage 20 becomes lower faster than the pressure in the space of the spring 26 (pressure on the outlet 13 side). Therefore, the force applied to both end surfaces of the valve body 24 is in the completely opposite direction to that when the compressor is rotating, and the valve body 24 moves upward in the figure, and as shown in FIG.
5. The flow of the oil passage 21 and the circumferential groove 17 is blocked by the upward shift of the circumferential semicircular groove 25 of the valve body 24, and the lubricating oil 23 under pressure due to the residual discharge pressure is inside the vane bottom and the cylinder. Stop the flow to.

As time passes, the residual pressure on the high pressure side is balanced through an expansion valve (not shown) provided in the evaporator (not shown), and eventually the pressure in the suction port 6 provided in the cylinder and the discharge The pressures in outlet 7 become equal.

In the above-mentioned long-term stop, the force applied to both end faces of the valve body 24 is equal, but the force exerted on the valve body by the spring 26
4 is held upward to prevent the oil passage from being re-opened. Although the purpose of the spring 26 is as described above, the spring 26 can be omitted in the configuration of the valve mechanism.

The force that moves the valve body 24 is the product of the area of the end face of the valve body 24 and the pressure to which the end face is subjected. Therefore, if there is excess or deficiency in the pressure and the movement of the valve body 24 becomes uncertain, the end area of the valve body 24 may be changed, for example, a stepped valve body with different diameters or a conical valve body at one end may be used. Adjustment is possible by this.

Effects of the Invention As is clear from the above description of the embodiments, according to the present invention, the lubricating oil supplied to the bottom of the vane groove is supplied and stopped based on the difference between the pressure on the compression space side and the pressure on the oil separation chamber side in the cylinder. Since the control is performed using a variable valve body, the supply of lubricating oil can be reliably stopped when the compressor is stopped. Therefore, lubricating oil can be prevented from flowing into the cylinder when the compressor is stopped, and oil compression can be prevented when the compressor is restarted.

In addition, since the present invention directly utilizes the pressure difference that inevitably arises from the state of the rotor, its operation is reliable and highly reliable.

[Brief explanation of the drawing]

Figure 1 is a side sectional view of a vane rotary compressor, Figure 2
The figure is a sectional view taken along the line AA in FIG. 1, and FIGS. 3 and 4 are sectional views of a valve body used in a compressor, each showing different operating states. 1...Rotsuta, 2...Cylinder, 3...Front side wall, 4...
Rear side wall, 5... Vane, 8... Discharge valve, 16... Vane groove, 17... Circumferential groove, 20... Passage, 21, 22... Oil passage, 24... Valve body.

Claims (1)

[Claims] 1 A cylindrical cylinder having a discharge port and a refrigerant suction port and both ends of which are closed by a front side wall and a rear side wall, a rotor that is arranged eccentrically within this cylinder and can freely rotate, and a plurality of cylinders formed on this rotor. a vane groove;
vanes that are provided in these vane grooves so as to be freely retractable and that their tips abut against the inner surface of the cylinder to partition the inside of the cylinder into a compression space that communicates with the discharge port and a suction space that communicates with the refrigerant suction port; a discharge valve that is provided at the discharge port and opens when the pressure in the compression space reaches a predetermined value; an oil separation chamber that covers the discharge port and the rear wall and has a refrigerant outlet; and a rotor side of the rear wall. an annular circumferential groove provided on the inner surface and located on the rotation trajectory of the bottom of the vane groove; an oil passage provided on the rear side wall communicating the oil separation chamber and the circumferential groove; Equipped with a valve storage hole provided in the middle,
A valve body is slidably provided in the valve housing hole, one end of the valve body in the sliding direction in the housing hole communicates with the compression space, and the other end communicates with the oil separation chamber side, and the valve body The vane rotary compressor is configured such that the oil passage is blocked when the storage hole is located at one end, and the oil passage is communicated when the storage hole is located at the other end.