JP2590493B2 - Compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a compressor, and is effective when used as, for example, a refrigerant compressor of an air conditioner for an automobile.

[Prior art and problems]

2. Description of the Related Art Conventionally, in a refrigerant compressor for automotive air conditioning, a compressor portion and an oil reservoir are formed in a housing, and lubricating oil in the oil reservoir is supplied to an oil-supplied portion of the compressor portion through an oil supply passage. Was known (for example, JP-A-57-157093).

However, according to the study of the present inventors, it was confirmed that the required amount of lubricating oil fluctuates significantly depending on the usage of the compressor.

When the compressor is in a steady operation, it is not desirable that a large amount of lubricating oil is supplied to the compressor unit side, and that a large amount of lubricating oil is discharged from the compressor during the refrigeration cycle. That is, in such a case, the lubricating oil circulating in the refrigeration cycle together with the refrigerant reduces the cooling efficiency in the refrigeration cycle. On the other hand, when the compressor has a high load and a low rotation speed, a large amount of lubricating oil needs to be supplied in order to maintain a smooth operation of the compressor.

As described above, the required amount of lubricating oil is changed in the compressor in accordance with the state of use.

In view of this, the present invention has previously proposed variable control of the amount of lubricating oil supplied to the compressor as required (Japanese Patent Application No.
-206223).

[Problems to be solved by the invention]

The present invention relates to an improvement of a compressor previously proposed by the present inventors, in which the amount of lubricating oil supplied to a compressor unit can be variably controlled as required by the compressor. It is an object of the present invention to continuously change the amount of lubricating oil to be supplied in accordance with the operation state of the vehicle.

(Configuration and operation)

In order to achieve the above object, in the compressor of the present invention, the compressor and the oil reservoir are formed in the housing, and the compressor and the oil reservoir are partitioned by the side plate. A spool valve through which an oil supply passage passes is provided in the side plate, and the oil supply passage is opened at the lower end of the spool valve and below the oil reservoir. The spool valve moves up and down under the influence of the pressure on the high pressure side of the compressor section, so that the opening end of the oil supply passage moves up and down. In other words, the higher the high-pressure side pressure, the lower the opening end of the oil supply passage, so that a large amount of lubricating oil is supplied to the compressor section.

Here, the high-pressure side pressure of the compressor section fluctuates greatly according to the use environment in which the compressor is placed. That is, when the compressor performs a high-load operation, the high-pressure side pressure increases accordingly. Therefore, according to the compressor of the present invention, when the compressor is in the high load operation state and the high pressure side pressure is high, the spool valve is displaced downward to a position corresponding to the pressure, and the amount of lubricating oil corresponding to the operation state is increased. Supply. That is, the operating state of the compressor is sensed by the high-pressure side pressure, and it is possible to continuously variably control the lubricating oil supply amount according to the operating state.

〔Example〕

Hereinafter, an embodiment of the compressor of the present invention will be described with reference to the drawings. In FIG. 1, reference numeral 2 denotes a cylinder housing which has a cylindrical shape and forms a cylinder space 101 therein. Reference numeral 3 denotes a front side plate for sealing a front opening end of the cylinder housing, and reference numeral 4 denotes a rear side plate for sealing a rear opening end of the cylinder housing. Bearings 102 and 103 are fixed to the front side plate 3 and the rear side plate 4, respectively, and the shaft 7 and the rotor 5 are rotatably supported by the bearings. That is, the rotor 5 is eccentrically arranged in the cylinder chamber 101 and rotates in the cylinder space 101. Further, a vane groove is formed in the rotor 5 so as to penetrate in the diameter direction, and the vane 6 is slidably disposed in the vane groove. The vane 6 has its tip slidingly contacting the inner surface of the cylinder space 101. Therefore, the compression chamber 108 is formed by the outer periphery of the rotor 5, the inner surface of the cylinder space 101, and the side surface of the vane 6.

Reference numeral 110 denotes a front housing disposed on the front side of the front side plate 3, and forms a suction chamber 111 between the front housing and the front side plate 3. The suction chamber communicates with an evaporator (not shown) of the refrigeration cycle via a suction service valve 8. Low-temperature and low-pressure refrigerant is sucked into the suction chamber 111 via the suction service valve 8 by the evaporator. Reference numeral 113 denotes a shaft seal disposed in the front housing 112, which prevents the refrigerant and the lubricating oil from flowing out along the shaft 7.

Reference numeral 12 denotes an oil reservoir housing provided behind the rear side plate 4 and has an oil reservoir 13 formed therein. The oil reservoir housing 12 is connected to the rear side plate 4, the cylinder housing 2, the front side plate 3, and the front housing 110 by through bolts 115.

Reference numeral 1 denotes a discharge chamber cover disposed on the side of the cylinder housing 2 and has a discharge chamber 119 formed therein. The discharge chamber 119 communicates with the compression chamber 108 via the discharge hole 10. That is, the discharge hole 1 is located at a position where the volume of the compression chamber 108 is reduced.
0 is open, and the high-temperature and high-pressure refrigerant is discharged into the discharge chamber 119 through the discharge hole 10. On the discharge chamber 119 side, the discharge valve 11
Are arranged. Further, the discharge chamber 119 communicates with the oil reservoir 13 through a communication hole 121 formed in the rear side plate 4.

The refrigerant discharged from the discharge chamber 119 toward the oil reservoir 13 separates the lubricating oil from the refrigerant due to the rapid expansion of the volume. The separated lubricating oil is stored below the oil reservoir 13, and the refrigerant from which the lubricating oil has been separated is discharged from the discharge service valve 15 to the condenser side (not shown) of the refrigeration cycle.

A cylindrical space 400 having an inner diameter of about 10 mm is formed in the rear side plate 4.
Are slidably disposed. A portion of the cylindrical space 400 that faces the upper surface 211 of the spool valve 21 serves as a first pressure chamber 410, and receives a rear end side pressure of the rotor 5 via the pressure guiding passage 25. The spool valve 21 has a stepped cylindrical shape, and a portion of the cylindrical space 400 facing the stepped portion 212 is a second pressure chamber 411. The pressure on the suction side of the compressor is introduced into the second pressure chamber 411 via a pressure guiding passage 420. The first oil supply passage 2 is provided in the small diameter portion 220 of the spool valve 21.
2, one end of the first oil supply passage 22 is open to the lower end 201 of the small diameter portion. The small diameter portion 220 projects downward from the opening 410 on the lower surface of the rear side plate 4, and
The small-diameter portion lower end 201 is exposed in the lubricating oil in the oil reservoir 13. Also, on the outer periphery of the large diameter portion 230 of the spool valve 21,
An annular groove 214 is formed, and the other end of the first oil supply passage 22 communicates with the annular groove 214. This annular groove 214 connects the first oil supply passage 22 and the second oil supply passage 20 when the spool valve 21 is displaced downward by a predetermined amount as shown in FIG. Therefore, the first and second oil supply passages 22 and 20 allow the compressor 100
And the oil reservoir 13 are communicated with each other. That is, the opening 208 on the compressor section 100 side of the second oil supply passage 20 is open at a portion corresponding to the suction stroke in the compression chamber 108, and the lubricating oil supplied through the first and second oil supply passages 22 and 20 is provided. As a result, the vane 6 and the rotor 5 are lubricated. The above-described pressure guide passage 420 introduces the suction side pressure through the second oil supply passage 20. First refueling passage 22
The open end 201 of the oil reservoir 13 is exposed in the oil reservoir 13 as described above. become. As a result, the liquid level of the lubricating oil in the oil reservoir 13 fluctuates according to the displacement of the opening end 201. That is, as is clear from FIGS. 3 and 4, when the open end 201 is displaced downward, the liquid level S is also lowered accordingly. Here, the volume of the oil reservoir 13 is set to a size such that about 40 cc of lubricating oil remains when the spool valve is slightly displaced downward as shown in FIG. Also, as shown in FIG. 4, the size is set such that about 10 cc of lubricating oil remains when the spool valve 21 is displaced downward. In this example, the stoke from the state where the spool valve 21 is displaced most upward (FIG. 2) to the state where it is displaced most downward is about 20 mm.

A spring 23 is provided on the stepped portion 212 of the spool valve 21, and the spring 23 presses the spool valve 21 upward in the drawing with a predetermined urging force.

Next, the operation of the above-described compressor will be described. When the driving force of an automobile driving engine (not shown) is received via an electromagnetic clutch (not shown), and the shaft 7 rotates, the rotor 5 rotates in the cylinder chamber 101. With the rotation, the volume of the compression chamber 108 repeatedly increases and decreases. At the part where the volume of the compression chamber 108 expands, the refrigerant is sucked into the compression chamber 108 from the suction chamber 111 through the suction hole 9. Further, as the volume of the compression chamber 108 decreases, the refrigerant in the compression chamber is compressed, and when the pressure rises to a predetermined pressure or higher, the discharge valve 11 is pushed open, and the discharge hole 10 is opened.
The liquid is further discharged to the discharge chamber 121. The refrigerant discharged into the discharge chamber 119 is discharged to the condenser side of the refrigeration cycle via the oil reservoir 13.

Here, it is necessary that the oil supply passage 20 be closed when the compressor is stopped. That is, if the lubricating oil in the oil reservoir 13 flows into the compression chamber 108 at the time of stopping, not only does the liquid compression occur at the start of the compressor, which requires a large starting torque, but also impairs the durability of the compressor. It will also be.

By the way, the spool valve 21 of the present embodiment opens and closes the passage based on the pressure of the pressure guiding passage 25 formed in the rear side plate 4, and the pressure guiding passage 25 is connected to the rear end of the rotor 5. Side, and is affected by the pressure on the high pressure side of the compressor. That is, the pressure guiding passage 25
At the opening, a pressure approximately midway between the low pressure side pressure and the high pressure side pressure of the compressor unit 100 is obtained.

Here, when the compressor is stopped, the entire refrigeration cycle is equalized, and the pressure on the suction side rises to about 6 atm. At the same time, the high pressure also drops to about 6 atm. As a result, when stopped, both the suction pressure and the high pressure are balanced at about 6 atm.
Therefore, the intermediate pressure generated at the end face of the rotor 5 also decreases to about 6 atm. Therefore, the first pressure chamber is
The intermediate pressure introduced into the pressure chamber 410 and the suction side pressure introduced into the second pressure chamber 411 via the pressure guiding passage 420 are balanced, and the spool 2
As shown in FIG. 2, the spool valve 21 is displaced to the uppermost position by the urging force of the spring 23 because the pressures acting on the upper and lower portions 1 are balanced. In this state, the annular groove 214 of the spool valve 21 is separated from the second oil supply passage 20, and the second oil supply passage 20 is closed.

Therefore, when the compressor is stopped, the lubricating oil in the oil reservoir 13 does not flow toward the compressor 100.

When the compressor starts and reaches steady rotation, the pressure on the low pressure side becomes 2
To about 3 atmospheres, while the pressure on the high pressure side is 12 ~
It rises to about 14 atm. Therefore, the intermediate pressure on the back of the rotor 5 also increases to about 9 atm. As the pressure increases, the intermediate pressure guided from the pressure guiding passage 25 to the first pressure chamber 411 is applied to the upper surface 211 of the spool valve 21. At the same time, the suction side pressure guided to the second pressure chamber 411 from the pressure guiding passage 420 is applied to the stepped surface 212 of the spool valve 21. As a result, the spool valve 21 is pushed down by a predetermined amount as shown in FIG. In this case, the annular groove 21 formed in the spool valve 21
4 connects the first oil supply passage 22 and the second oil supply passage 20. Accordingly, the lubricating oil in the oil reservoir 13 is supplied to the low-pressure side compression chamber 108 via the oil supply passage 208. By supplying lubricating oil to this portion, smooth rotation of the rotor 5 is ensured. Here, since the opening 201 of the oil supply passage 22 is opened at a position at a predetermined height from the bottom of the oil reservoir, even if the lubricating oil is supplied from the oil supply passage 22 to the compressor unit 100 side, the predetermined amount is still maintained. The lubricating oil (about 40 cc in this example) is stored in the oil reservoir 13.

In other words, a large amount of lubricating oil is prevented from flowing out of the discharge service valve 15 to the refrigeration cycle. here,
Since the lubricating oil does not contribute to the cooling capacity of the refrigeration cycle, circulating a large amount of the lubricating oil through the refrigeration cycle is not desirable in terms of the cooling capacity. In this regard, in the compressor of the present embodiment, since a certain amount of lubricating oil is always held in the oil reservoir 13, it is necessary to prevent the decrease in the cooling capacity of the refrigeration cycle while smoothly lubricating the compressor. Can be.

Depending on the usage of the refrigeration cycle, the load applied to the compressor may be particularly high. For example, it is a state where a car is running at low speed in summer. In this state, the cooling load is extremely large, and the rotational speed of the compressor is also low. As a result, the pressure on the high pressure side may increase significantly and reach 20 atm or more. Further, the pressure on the suction side also increases to about 3 to 4 atm. That is,
In such a state, the intermediate pressure rises to about 11 to 12 atm. Therefore, as shown in FIG. 4, the pressure applied to the upper surface 211 of the spool valve 21
Is displaced to the bottom. With this displacement, the oil supply passage
The position of the opening 201 of 22 is also continuously displaced downward to near the bottom of the oil reservoir.

Here, the diameter of the large diameter portion 230 of the spool valve 21 is, for example, 1
It is about 0 mm, while the diameter of the small diameter part 220 is, for example, 4 m
m. Since the gap between the small diameter portion 220 and the hole provided on the rear side is set to about 40 μm,
The spool valve 21 is not pushed up again in the drawing by the pressure in the oil reservoir 13.

During high load operation of the compressor, lubrication of the compressor is particularly important. Therefore, it is important to supply a sufficient amount of lubricating oil to the compressor even if the cooling capacity of the refrigeration cycle is somewhat reduced. In the compressor of this embodiment, the spool valve 21 is further displaced downward as shown in FIG. 4, so that the lubricating oil remaining in the oil reservoir 13 is continuously displaced in accordance with the downward displacement. Side. Therefore, even in such a high-load operation state, problems such as seizure of the compressor can be satisfactorily prevented.

In the above-described example, a piston-like valve that reciprocates in the rear side plate 4 is adopted as the spool valve, but it is a matter of course that another type of valve may be used. Further, the signal pressure for driving the spool valve does not necessarily have to be the above-described intermediate pressure. Any pressure may be used as long as it is affected by the high pressure side pressure of the compressor. In other words, the signal pressure may be any signal pressure that can determine whether the compressor is in the steady operation or the high load operation.

〔The invention's effect〕

As described above, in the compressor of the present invention, the oil supply passage opening end position is variably controlled in accordance with the operation state, so that the compressor can be smoothly lubricated over a wide range.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an embodiment of the present invention, and FIGS.
The figure is a sectional view showing the operating state of the switching valve shown in FIG. 2 ... Cylinder housing, 4 ... Rear side plate, 5
…… Rotor, 6 …… Vane, 12 …… Oil reservoir housing, 13…
... oil reservoir, 21 ... switching valve.

Claims (1)

(57) [Claims] 1. A housing having a compressor portion and an oil reservoir therein, a side plate disposed in the housing to partition the compressor portion and the oil reservoir, and formed on the side plate in a vertical direction. A spool valve slidably disposed in this space and having a lower end facing the oil reservoir, and a spool formed in the spool valve and having one end extending from the lower end of the spool valve to the oil reservoir. A first oil supply passage having the other end communicating with the side surface of the spool valve, and a second oil supply passage formed in the side plate, one end of which opens into the space and the other end of which communicates with an oiled portion of the compressor unit. A pressure chamber formed above the spool valve in the space and configured to introduce a pressure related to a high pressure side of the compressor, wherein the spool valve corresponds to a pressure related to a high pressure side of the compressor unit. Changes up and down Compressor, characterized in that changing the position of the one end side open end of the first oil supply passage.