JPS6365188A - Vane-type compressor - Google Patents

Abstract

PURPOSE:To keep off any backflow of oil to the inside of a compression space at the time of compressor stoppage, by forming a pressure control valve, being opened or closed by differential pressure between pressure in the intermediate pressure port installed on a locus of the vane groove bottom and lubricating oil pressure in a discharge chamber, in an oil feeding passage. CONSTITUTION:An oil feeding passage 23, feeding oil to a back pressure chamber of a vane 4 and other sliding parts, is formed in a rear side plate 2 of a vane-type compressor via a needle bearing 7. In this oil feeding passage 23, there is provided with a pressure control valve 40. At the head side of a piston 40b of this pressure control valve 40, there is provided with an interconnecting port 40d leading lubricating oil 22 in the chamber bottom into a cylinder chamber 40e, and at the opposite side, there is provided with an interconnecting port 39 introducing pressure in the intermediate pressure port 32 installed on a locus of a vane groove bottom part. With this constitution, the pressure control valve 40 is opened or closed in good responsiveness owing to differential pressure with pressure of the lubricating oil 22 on the bottom of pressure chamber inside the intermediate pressure port, cutting off the oil feeding passage 23 at the time of compressor stoppage, and thus a backflow of oil to the inside of the compressor is positively prevented from occurring.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a vane compressor used in automobile air conditioners, etc., and is particularly suitable for improving the durability of the compressor and reducing A noise. related to vane backpressure control.

[Conventional technology]

Conventional vane backpressure control, as described in Japanese Patent Application Laid-open No. 192891/1983, involves lubricating oil stored at the bottom of the chamber being collected by both the low-pressure port and the high-pressure port through an oil supply passage installed on the rear plate. Therefore, immediately after the compressor is stopped, when the pressure inside the compressed liquid is balanced, the oil at the bottom of the chamber on the high pressure side flows through the above-mentioned oil passage into the compression chamber on the low pressure side (the two opposing vanes). The oil flows into the space formed by the outer peripheral surface of the rotor and the inner peripheral surface of the cam ring, and the inside of the same chamber is filled with oil.

Further, Japanese Patent Application Laid-Open No. 59-12192 discloses a refueling stop device in a screw compressor that utilizes the differential pressure between the two-force pressure of a large gas throttle valve and the discharge pressure of the compressor.

[Problem that the invention seeks to solve]

However, since conventional devices utilize changes in suction pressure, V
This takes a long time (several seconds) and the response to stop refueling is poor. It is possible to increase the spring force in order to improve the response of refueling stop, but since it becomes difficult to open the 6-oil stop device, it is necessary to increase the spring force after starting until the discharge pressure reaches a predetermined value. The square is opened, and the lag in the mountains is brought to life.

Therefore, in the structure of the prior art described above, the compressor is started with oil accumulated in the compression chamber. This will cause deformation of the cam ring contact/rue (where the rotor outer circumferential surface and the cam ring inner circumferential surface are closest), irregularities in the vane and cam ring, and compress the oil. There was a problem that the habitability was impaired due to abnormal noises.

The purpose of the present invention was to improve the above points, and it is possible to instantly prevent the backflow of oil from the high pressure side into the compression chamber and to eliminate oil supply delays, thereby improving reliability and comfort. The aim is to provide a high vane expansion pressure and compression machine.

[Means for solving problems]

The above purpose is to install a pressure control valve that operates based on the differential pressure between the internal pressure and the intermediate pressure in the oil supply passage of the rear plate.
This is accomplished by the pressure control valve closing the oil supply passage immediately after the compressor stops, thereby preventing oil from flowing back into the compression chamber from the bottom of the chamber.

[Effect]

The pressure control valve detects the pressure inside the chamber (this pressure is the same as the compressor discharge pressure) and other pressures (e.g., suction chamber pressure, compression chamber pressure, and intermediate pressure port pressure). The oil supply passage is configured to close when the pressure difference between the chamber internal pressure and another pressure is smaller than a set value of the pressure control valve, and to open the oil supply passage when the pressure difference is larger than the set value. . Therefore, the old backflow into the compression chamber when the compressor is on the hour? It can be prevented.

〔Example〕

DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. FIGS. 1 and 2 show a vane compressor according to the present invention. A rotor having a plurality of plates 74 movable in the radial direction in a chamber formed by a front side plate 1, a rear sub-plate 2, and a cam ring 3 fastened between them by bolts (not shown). 5 is attached to a drive shaft 6 provided at the center of the compressor, and is horizontally mounted.

, the drive @67 is supported by the front plate 1 and the rear grate 2 by needle bearings 7.

Further, the front side plate 1, rear side plate 2, and cam ring 3 are fixed to the front cover 8 by through bolts (C shown in the figure).

The front cover 8 and the chamber 9 are kept airtight with an O-ring 1o, and the rotor 11 and the front cover 8 are covered with a metal chamber 9.
A space 13 is formed at the rear of the a 11111 plate 2 shown in q, which forms a shaft seal with the cover plate 12 fixed to the front cover 8. An oil separator 414 is installed to cover it.

Next, to describe the flow of the refrigerant flowing into the compressor, the refrigerant that has returned to the compressed rock from the refrigeration cycle (not shown) is passed through the pure silk rock inlet 15 formed in the front cover 8 to the front cover. It flows into the formed low pressure passage 16. The refrigerant is supplied to the intake air hole 17t- which is provided on the front side plate 1.
The air flows into the compression chamber 18, which is formed by two adjacent vanes, the outer circumferential surface of the rotor, and the inner circumferential surface of the cam ring. The compression body ram first changes from 0ρ to maximum ρ due to the rotation of the drive shaft 6, and ends at 0 anchor for intake. Furthermore, due to the rotation of the drive shaft V, the compression of the silkworm body decreases from the maximum value, so that there is no compression. The refrigerant that has reached the compressed discharge pressure passes through the discharge port 19 and the discharge tank 20 provided in the cam ring 3, and then passes through the ζ field molecule @4.
At this point, the oil is separated and only the refrigerant is sent under pressure to the refrigeration cycle through a compressor discharge port 21 provided in the refrigerator 9.

Lubricating oil 2 under discharge pressure separated by oil separator 14
2 is stored in the chamber 9 after the oil is stored at the bottom of the chatuba.
Due to the differential pressure between the internal pressure and the internal pressure of the compression chamber 18, the oil supply passage 23 and the pressure control valve 40 formed in the rear plate 2 are
The pressure flows through a ring-shaped communication passage 301 provided on the outer periphery of the needle bearing 7, and flows into a high-pressure port 31 formed in such a way as to communicate with the passage.

As shown in FIG. 2, the high pressure hoard 31 is shaped so that the vane groove bottom 27 touches the high pressure port at the point when the base end of the vane approaches the discharge port 193 of the cam ring. The port 31 is supplied with lubricating oil under the discharge pressure, and the force that presses the vane 4 against the inner circumference of the ring (hereinafter referred to as vane back pressure) is equal to the discharge pressure. On the other hand, the intermediate pressure ports 32 and 33 formed in the front plate 1 and the rear plate 2 are located 180° symmetrically about the sliding shaft 6; (formed in a fan shape 8, For the purpose of ensuring a compressed 1-man residence.

Same as above with the center of the rotor with a half-inch slightly larger than the outer diameter of the rotor.
When the tip of the vane reaches the end point in the rotor rotation direction of the cam ring arc provided at K, the bottom part 27 of the vane (+) opens to the intermediate pressure port.In other words, the vane 4 In this section, the vane is recessed into the rotor as it passes through the arc of the cam ring), and at the point when the vane pops out from inside the rotor, the pressure inside the low pressure port is applied as vane back pressure. That is, if a layer is formed at the bottom of the vane groove, when the tip of the vane reaches the discharge port, the lower part communicates with the high pressure port, and at the starting point position of the cam ring arc part in the rotor rotation direction, it separates from the 1 pressure port, and the same arc The part does not communicate with the intermediate pressure and high pressure ports,
At the end point of the arc, it communicates with the low pressure port again.

The pressure inside the intermediate pressure port is determined by the switching action at the bottom of the vane source (the bottom of the vane groove opens and closes communication between the high pressure port and the intermediate pressure port), and the pressure inside the intermediate pressure port is determined by the switching action at the bottom of the vane source (the bottom of the vane groove opens and closes communication between the high pressure port and the intermediate pressure port). The optimum value can be obtained depending on the shape, the performance of the compressor, and the ease of assembly (for example, the gap between the rotor and the cam ring, the gap between the rotor end face and both plates, and the gap between the vane end face and both plates).

The oil flowing into the intermediate pressure ports 32 and 33 is used as vane back pressure for each vane, and after lubricating the needle bearings 7 installed on both plates, it passes through the gap between the plate, rotor, and vane. , flows out into the compression chamber 18.

3 and 4 show detailed sectional views of the pressure control valve 40 installed on the rear plate 2. FIG. The pressure control valve 40 includes a cylinder 40a with a flange, a piston 40b, and a spring 40C inserted inside the piston 40b. The cylinder 40a is provided with a communication hole 40d for introducing the lubricating oil 22 at the bottom of the chamber into the cylinder chamber 40e. Please note that the cylinder 40a is fixed to the rear plate 2 with screws (J not shown).
The cylinder 40a and the rear plate 2 are connected to an O-ring 40f.
and sealed with 40g. A ring J having a flow path area smaller than that of the oil supply passage 23 is provided on the outward surface of the piston 40b.
40h is provided, and the piston 40b reciprocates by the elastic force of the spring 40C and the fluid force to open and close the oil supply passage provided in the rear plate 2. Poor,
At the bottom of the piston 40b (the left end of the piston in FIGS. 3 and 4), there is a first outlet hole 39 for introducing pressure other than the upper discharge blade (selection of this pressure will be explained later). , holes are provided in the rear plate 2.

Next, a description will be given of the pressure gauge leading to the passage hole 39.

Figure 5 is a four-dimensional experimental curve diagram showing how the discharge pressure P4, intermediate pressure port pressure PbL, and pressure P change with time t after the pressure pump is stopped. be. , according to FIG. 5, 1=1. This was the time when Inaiso was stopped. Here, PbL during operation of the compressor
has a value K fi# approximately equal to (P-+-P,)/2. The flexibility required for the pressure control fF40 is as follows: (1) The oil supply passage must be closed immediately after the compressor is stopped. i2) When restarting the pressure return mechanism Vζ
, it will not work unless the above 1 oil supply passage is 1.4 (chattering of the vane occurs due to the lower part of the vane back pressure)
. Therefore, in order to satisfy the condition (1), as shown in FIG. 5, the intermediate pressure port pressure PbL is optimal as the pressure source for guiding the +mm passage hole 39 (as shown in FIGS. 1 and 2). Therefore, as a result of experimental studies on conventional compressors,
To avoid the problems of the prior art described above, Δt=t2−
1. ≦4 directions.

It became clear that JP=Pa-PbL=2~(Ky/cM12). Therefore, the setting position of the spring 40c used in the pressure control valve 40 should be set so as to satisfy both the above condition and the condition (2) above. The operation of the pressure control valve configured as above will be explained. In FIG. 4, when the compressor stops, spring 40c
If the spring force is kFc, then Pc>ΔP-Ap where LAP is the end of the head surface of the piston 40b, the piston 40b is pushed up by the spring 40C, and the oil supply passage 23 is pushed up by the spring 40C. Ru. Therefore, the lubricating oil stored at the bottom of the chamber is transferred to the compression chamber 1.
Will it flow into 8? Prevention is the monkey. Next, when the cough compression area is raised again from this state, it becomes as shown in FIG. 3.

Therefore, the piston 40b is pushed down by the differential pressure ΔPk, and the ring groove 4011 provided on the outer periphery of the piston communicates with the oil supply passage 23, so that @lubrication 22 is supply 5 exit passage 2
3. It communicates with the intermediate pressure port through the communication passage 30 of the needle bearing 7 and the pressure control ports 31 and 32.

Therefore, according to the four examples, the vane back pressure can be obtained without any problem even when the rice compaction machine is restarted, and the response of the pressure control valve is improved.

6 and 7 illustrate other embodiments of the invention.

The passage hole 39 for guiding the pressure to the pressure control valve 40 is compressed for 18 yen.
is connected to. The pressure P in the compression chamber 18 changes in the range P, ≦P, (Pa) as the drive shaft rotates.

Since the pressure control valve 40 and the compression chamber 18 are close to each other via the rear plate 2, the passage hole 39 is
FIG. 8 shows another example of the present invention, in which a check valve 5o is installed at the inlet 15 of the front cover 8. The passage hole 39 includes a passage hole 39a in the rear plate 2, a stepped passage hole 39b in the cam ring 3, and a passage hole 39c in the front plate 1.
It has a pressure of 4 degrees and communicates with a low pressure path 16 formed in the front cover 8. The configuration other than the above is the same as in FIG. 1. Therefore, immediately after the compressor is stopped, the rise in the low-pressure passage internal pressure P m' is caused by the upward f? From the sentence lc, Ps' shown in Figure 5 is set.
Q pressure rises and becomes an old man, rjiJ lewd JP =
Pa-P,' = 2-4 to 9/L: 1n''.

Δt≦4 daughter gold ten public gold is enough.

Therefore, according to the invention, the responsiveness of the pressure +l1lJ elevation valve can be improved.

〔Effect of the invention〕

As mentioned above, according to the uninvented method, it is possible to prevent oil from flowing into the pressurizer immediately after the compressor stops, and since its LE and solubility can be the same as above, the compressor's It has the effect of improving air flow and providing a vane expansion compressor with high air flow.

[Brief explanation of the drawing]

Fig. 1 is a side sectional view showing an embodiment of the invention, Fig. 2 is a sectional view taken along line 1-1 in Fig. 1, and Figs. 3 and 4 are pressure crabs! i
il *Detailed analytical surface diagram of the J'J valve, Figure 5 is an experimental curve diagram showing each pressure change with respect to time after the compressor is stopped, Figures 6 and 7 are other uninvented examples. A side sectional view and a sixth
FIG. 8 is a cross-sectional view showing an embodiment of the present invention. 1...Front side plate, 2...Rear side plate,
3... Cam ring, 4... Vane, 5... Rotor, 8... Front cover, 9... Chamber, 13...
...Space part, 18...Compression chamber, 22...Lubricating oil, 2
3...Refueling passage.

Claims (1)

[Claims] 1. A cam ring equipped with an intake port and a discharge port, an operating chamber formed by the cam ring, a rear plate and a front plate installed to close both sides of the cam ring, a plurality of vanes that can move forward and backward in the radial direction, and a rotor having a plurality of vane grooves in which vanes are disposed and installed in the working chamber so as to be rotatable about the axial center of the cam ring; and a space formed at the rear of the rear plate; a chamber for storing lubricating oil under discharge pressure;
a front cover having an inlet; a passage hole communicating with the lubricating oil on at least one of the rear side or front side plate; a high pressure port communicating with the passage; and a high pressure port on both plates. 1. A vane type compressor equipped with an independent intermediate pressure port, characterized in that a pressure control valve operated by a pressure difference between the discharge pressure and the intermediate pressure port is installed in the passage.