JPS5836194B2 - vane compressor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vane compressor for vehicle air conditioning.

In conventional vane compressors, oil is pumped up from an oil reservoir chamber provided at the bottom of the machine body by an oil pump driven via a drive shaft, and is also pumped up to the drive shaft or rotor (through an oil supply hole provided in this section). It is common to lubricate sliding surfaces with vanes or bearings by forcibly feeding them.

As is generally known, the space in the engine room of a vehicle is naturally limited, and therefore the external dimensions of the compressor installed in the engine room are required to be as small as possible. There is.

However, in conventional compressors, an oil storage chamber is provided at the bottom of the fuselage to store oil, and a mechanical oil pump is built into the fuselage, resulting in an increase in the external dimensions of the fuselage and the above-mentioned problems. In addition, the system in which oil is pumped up from the oil reservoir chamber using an oil pump and supplied through the oil supply hole provided in the drive shaft or rotor has a complicated structure (there were problems such as curling, etc.). The invention provides a single-pan type compressor that uses blow-by gas to satisfactorily lubricate the sliding surfaces of movable members without using an oil pump by providing an oil reservoir in the center of the rotor. The purpose is to provide a more compact aircraft and simplify its structure.

Hereinafter, illustrated embodiments embodying the vane compressor of the present invention will be described in detail.

The outer shell of the compressor is composed of a cylindrical center housing 1, and a front housing 2 and a rear housing 3 connected to both front and rear ends of the center housing 1.
The cylindrical hole of the center housing 1 is eccentric with respect to the center C of the circular space of the front housing 2 and the rear housing 3, and an iron sleeve 4 is fitted on the inner circumferential surface of the cylindrical hole.

Note that this sleeve 4 may be integrally formed with the center housing 1 itself.

Inside the housings 1 and 2.3 (in this case, the front and rear end plates 5 and 6, which are formed in a disc shape, are in close contact with the end surfaces of the sleeve 4 and are respectively concentric with the center of the circular space of the front housing 3). is housed in
The front end plate 5 is attached to the front housing 2
The drive shaft 8 is fitted onto one end of a drive shaft 8 which is rotatably supported via a bearing 7, and is fixed with a pin 9 (troweled), and the rear end plate 6 is rotatable via a bearing 10 on the rear housing 3L. It is supported.

Therefore, inside the housing 1, 2.3 is a low pressure chamber 11 surrounded by the front housing 2 and the front end plate 5, and a low pressure chamber 11 surrounded by the rear housing 3 and the rear end plate 6. It is separated into a chamber 12 and a space surrounded by both end plates 5, 6 and the sleeve 4 of the center housing 1, and within this space, a cylindrical rotor 13 has a part of its outer circumferential surface covered with a sleeve. It is eccentrically housed so as to be in contact with the lower part of the inner peripheral surface of No. 4.

In this embodiment, the rotor 13 is arranged as shown in FIG.
It consists of a rotor element 13a divided into equal parts, and each rotor element 13a is fixed with its end face in close contact with the end plates 5, 6 by, for example, a through bolt 33 or the like.

Thus, a space surrounded by the outer peripheral surface of the rotor 13, the inner peripheral surface of the sleeve 4, and both end plates 5 and 6 is used as a compression chamber 14 for refrigerant gas, while the inner peripheral surface of the rotor 13 and both end plates 5 and 6 form a compression chamber 14 for refrigerant gas. , 6 and {The space surrounded by these is the oil reservoir chamber 15.

A guide groove 16 of a predetermined width is provided between the dividing surfaces of each rotor element 13a constituting the rotor 13, and each guide groove 1
6 has a vane 1 longer than the length (radial direction) of this groove.
7 is slidably inserted into the opposing vane 17.
The inner proximal end portions of each of the two ronds 18 are connected to each other and integrated.

Each vane 17 has a sliding groove 19 at its outer tip, and the sub vane 20 fitted into this sliding groove 19 contacts the inner peripheral surface of the sleeve 4 with an appropriate contact pressure. It is biased by a spring 21.

Each vane 17 slides within the guide groove 16 as the rotor 13 rotates, and its base end side enters and exits the oil reservoir chamber 15.

The compression chamber 14 communicates with a suction chamber 23 provided in the center housing 1 and having a suction hole 22 for return refrigerant through a number of suction ports 24 provided in the sleeve 4. The high-pressure refrigerant discharge holes 25, which are provided in 1 liter, are communicated through discharge ports 26, which are provided in 4 liters in the sleeve.

Note that 27 is a discharge valve provided at the discharge port 26.

28 is a gas vent hole provided through the drive shaft 8;
A substantially central portion of the oil reservoir chamber 15 and the front low pressure chamber 11 are communicated through a through hole 29 provided in the front end plate 5 .

Reference numeral 30 denotes a guide hole provided through the rear end plate 6, which communicates approximately the center of the oil reservoir chamber 15 with the rear low pressure chamber 12.

Reference numeral 31 denotes communication holes that are provided through the center housing 1 to communicate the low pressure chambers 11 and 12 with the suction chamber 23, respectively.

32 is a shaft seal. The vane compressor of this embodiment is constructed as described above, and when the end plates 5, 6 and rotor 13 are rotated together with the drive shaft 8 (clockwise in FIG. 1), the vane 17 is rotated. Make sure that the tip of the vane 20 is always in contact with the inner peripheral surface of the sleeve 4.
Since the guide groove 16l rotates in the compression chamber 14 while sliding along the guide groove 16l, the return refrigerant that flows into the suction hole 22 from the external circuit from the external circuit is compressed from the suction chamber 23 via the suction port 24. into the chamber 14 and then into the compression chamber 1
As the volume of refrigerant 4 gradually decreases, it is compressed and becomes a high-pressure refrigerant, which is sent out from the discharge port 26 through the discharge hole 25 to the external circuit.

In the oil reservoir chamber 15, the centrifugal force generated by the rotation of the rotor 13 causes the refrigerant gas containing a large amount of oil with high oil density or the oil separated from the refrigerant gas to collect near the outer peripheral wall. The refrigerant gas with low density is gathered in the central portion It!I.

Therefore, when the vane 17 sliding in the guide groove 16 with the rotation of the rotor 13 thrusts its base end into the oil reservoir chamber 15, both sides of the vane 17, which are sliding surfaces with the rotor 13, are exposed to the oil reservoir. Since it is exposed to the chamber 15, much of the oil in the refrigerant gas having a high oil density adheres to both side surfaces.

Furthermore, when the vane 17 slides toward the compression chamber 14 side, the sliding surfaces of both end plates 5 and 6 with the end surfaces of the vane 17 are partially exposed in the oil reservoir chamber 15, so oil is also applied to the sliding surfaces. It will stick.

Therefore, the sliding surfaces between the rotor 13 and the vanes 17 and the sliding surfaces between the end plates 5, 6 and the vanes 11 are supplied with oil as the vanes 17 slide, thereby achieving good lubrication.

On the other hand, the refrigerant gas with low oil density existing near the center of the oil reservoir chamber 15 is in the low pressure chamber 11, which has a lower pressure than the inside of the oil reservoir chamber 15.
12 through the guide holes 28 and 30 and the through hole 29, and are used to lubricate the bearings 7 and 10 and the shaft seal 32, and return to the suction chamber 23 through the communication hole 31.

Also, while the compressor is in operation, the pressure in the compression chamber 14 on the compression stroke side (right side in Figure 1) is considerably higher than the pressure in the oil reservoir chamber 15, so the pressure in the compression chamber 14 A portion of the refrigerant gas is transferred to the rotor 13 and vane 17 as blow-by gas.
The blow-by gas flows into the oil reservoir chamber 15 through the sliding surface of the rotor 13, and the oil is separated from the blow-by gas by the centrifugal force generated by the rotation of the rotor 13.

Furthermore, on the suction stroke side (the left side in FIG. 1), the pressure in the oil reservoir chamber 15 is slightly higher than the pressure in the compression chamber 14, so the refrigerant gas in the oil reservoir chamber 15 flows between the port 13 and the vane 17. Since the refrigerant gas flows into the compression chamber 14 from the sliding surface between the rotor 13 and the vane 17, the sliding surface between the rotor 13 and the vane 17 is also lubricated by the flow of refrigerant gas caused by such a pressure difference.

On the other hand, since the pressure within the oil reservoir chamber 15 is considerably increased by centrifugal force, this pressure increase reduces the flow rate of the blow-by gas flowing from the compression chamber 14 on the compression stroke side to the oil reservoir chamber 15 as described above. , a decrease in volumetric efficiency is suppressed, and even when the amount of oil in the oil reservoir chamber 15 decreases, most of the oil is collected toward the wall side by centrifugal force, so that the vane 17f described above is maintained even though the amount of oil is small. This effectively lubricates the sliding surfaces involved.

Additionally, when the compressor is suddenly started, a boiling phenomenon (a phenomenon in which liquid oil accumulated at the bottom of the oil reservoir chamber bubbles) may occur in the oil reservoir chamber 15. However, there is a risk that a large amount of oil in the oil reservoir chamber 15 will flow out to the low pressure chamber 11, 12 side, and the amount of oil in the oil reservoir chamber 15 will decrease significantly, causing insufficient lubrication of the sliding surfaces of the vanes 17. However, in this embodiment, the rotation of the rotor 13 (accompanying the rotation of the rotor 13 generates a centrifugal force within the oil reservoir chamber 15, and this centrifugal force acts to suppress the boiling phenomenon, thereby pushing the oil in the gas toward the wall of the oil reservoir chamber 15. In order to collect the oil to the side, the oil passes through the guide holes 28 and 30 and enters the low pressure chamber 11.
．． This prevents the lubricant from flowing to the 12 side, thereby preventing the occurrence of insufficient lubrication as described above.

As described in detail above, the present invention provides a vane type compressor C, in which an oil reservoir chamber is provided in the center of the rotor, and a vane is slidably attached to a guide groove of the rotor as the rotor rotates. By configuring the oil reservoir to move in and out, blow-by gas can be used to clean the sliding surfaces between the rotor and the vanes and the sliding surfaces between the vanes and the end plate without using a mechanical oil pump. In addition to providing good lubrication and preventing seizure, this is especially compared to conventional systems in which oil is pumped up from an oil reservoir at the bottom of the machine using an oil pump to supply oil to the sliding surfaces that need to be lubricated. Therefore, the external dimensions of the fuselage can be reduced to make it more compact, making it convenient for mounting in the engine room of a vehicle with a narrow space.Moreover, the structure is simple, which is extremely advantageous in terms of manufacturing.

In addition, the present invention (according to which the oil reservoir chamber is provided in the rotor),
Rotation of the rotor (thus, the centrifugal force generated in the oil reservoir can suppress the outflow of blow-by gas from the compression chamber as much as possible, reducing the drop in volumetric efficiency, and also reduce the boiling phenomenon in the oil reservoir during startup. Moreover, the amount of oil in the oil reservoir can be reduced (despite this, the sliding surfaces of the vanes can be effectively lubricated).

[Brief explanation of drawings]

The drawings show an embodiment of the present invention, and FIG. 1 is a front sectional view showing a vane compressor, FIG. 2 is a sectional view taken along the line ■-■ in FIG. 1, and FIG. It is a sectional view taken along the line -■. 1: Center housing, 5, 6: End plate, 13
: Rotor, 14: Compression chamber, 15: Oil reservoir chamber, 16: Guide groove, 17: Vane.

Claims (1)

[Claims] 1. A cylindrical housing, front and rear end plates that are closely and rotatably supported by the end face of the housing, and that rotate eccentrically within the space surrounded by the housing and end plates f. a rotor that can be housed in the rotor and has both ends fixed to the end plate; a plurality of guide grooves that extend through the rotor in the radial direction at predetermined intervals in the circumferential direction of the rotor; A plurality of vanes are slidably fitted into the guide groove so as to be in contact with the inner surface of the housing, and opposing vanes are connected to each other. A circular hollow oil sump chamber is provided which communicates with the suction chamber through a guide hole penetrated through the shaft center, and the vane is configured to move in and out of this oil sump chamber by sliding as the rotor rotates. A vane compressor that is characterized by: