JPS58138288A - Rotary compressor - Google Patents

Abstract

PURPOSE:To reduce the running/stopping frequency for regulating the delivery when compared with conventional one, by varying the delivery of a rotary compressor in accordance to the variation of the suction pressure of the rotary compressor. CONSTITUTION:When the suction pressure in a suction chamber 13 increases to overcome the spring load of a spring 34 in a second pressure responsive valve 27, a plunger 29 is pushed to the left to block a pilot pressure feed path 25. Consequently an intermediate pressure between the delivery pressure and the suction pressure of a compressor is provided in an intermediate chamber 26 and functions through said path 25 on the back face of a first pressure responsive valve 22 to move the valve 22 against the spring 24 and the pressure in an operating chamber 12 to the right then fitted with a return path 21 to block the return path 21 from the suction chamber 13. Consequently the compressor will run with maximum capacity of 100%. While when the suction pressure drops below the setting level, the return path 21 will onen to transfer the operation of about 50% capacity. Consequently the running/stopping frequency for the delivery regulation can be reduced.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a rotary compressor, and particularly to a rotary compressor useful as a refrigerant compressor for a cooler system for a motor vehicle.

The rotary compressor for compressing refrigerant used in the automotive Ku2 system is connected to the crankshaft of the Ennon via a general Kt & clutch. This rounding and compressor is 700~
It is used in a wide rotation speed range of 6000 rpm. However, the capacity of the pressure LiA machine is designed mainly to exhibit sufficient cooling capacity at low rotation speeds, but the cooling capacity tends to be excessive at high rotation speeds or low heat loads.

As described above, when the cooling capacity becomes excessively high, problems arise in that the suction pressure of the compressor decreases, the compression ratio increases, the efficiency of the compressor decreases, and the fuel efficiency of the automobile deteriorates.

The present invention has been made in view of the above problems, and is capable of reducing the discharge capacity of the compressor during high rotation, low heat load operation, and startup, and does not require a special control device.
It is an object of the present invention to provide a variable capacity rotary compressor that can continuously change the capacity.

Hereinafter, the present invention will be described in detail with reference to the drawings.

1 to 4 show examples of the present invention. In FIG. A 7W tonide plate 3 is disposed on the front end surface of the liner 20 (left end 1ffi in FIG. 1), and a rear side plate 4 is disposed on the rear end surface of the liner 20. The front end EfiK of Derate 3 is the front housing.
A rear housing 6 is provided on the rear end surface of the front side plate 3 to cover the liner 3 and the rear side plate 3. These front housings 5
゜Hunt side plate 3. Liner 2. Although not shown, the rear side plate 4 and the rear housing 5 are fixed together with a bolt.

A rotor 7 is eccentrically and rotatably provided within the liner 2, and a rotating shaft 8 integrally connected to the rotor 7 is supported by the front side plate 3 via a bearing 9. The rotation s8 extends outside the front housing 5, and the rotation shaft 8 is adapted to receive the driving force of the engine via an electromagnetic clutch (not shown). Between the rotating shaft 8 and the front housing 5, a ninth shaft device 10 is arranged to maintain a seal from the outside air.

As shown in FIG. 3, the 10-tough is provided with two vanes 11 which pass through its center and are slidable in the radial direction. Both ends of the vanes 11.1 and 711 are so arranged that they are always in sliding contact with each other by 1 m2 of 2 in.2 as the rotor 7 rotates. Rotor 7゜□ Here it is 4 due to liner 2 and nid grating 3.4
One operation If! 12 are formed. Each operation j112
is adapted to move and change its volume over and over again as it rotates throughout the day.

As shown in FIG. 2, an arcuate groove-shaped suction 1113 is formed on the front end surface of the first housing 5, and the compressed fluid drawn into this suction 1i113 from the suction port 14 is As shown in FIG. 3 and FIG. 3, the pump enters the volume increase stage through the suction port Is opened in the front knife plate 3 and is sucked into the actuator 1i112. That is, the fluid to be compressed at the suction pressure is filled into the actuator 1112 between the working chamber 12 and the suction port 1st. Then, the fluid to be compressed enters the working chamber 12 through the suction stage, and the fluid to be compressed enters the working chamber 12 into the working chamber 12.
Compressed with volume reduction of 120, working ml! When the internal pressure reaches the discharge pressure, it is discharged from the discharge port 16 into the discharge chamber 17 in the Ahunonda 6. 18 is a discharge valve, 1
9 is a valve stop A# 20 that regulates the opening amount of the discharge valve 180
is the discharge point to the outside.

The front side plate 3 is provided with a cylindrical compressed fluid return passage (hereinafter referred to as a return passage) 21. One end of the return passage 21 is connected to the working chamber 12.
The other end of the return passage 21 is open to the suction chamber 1BK.

22 is a round O first pressure-responsive valve that opens and closes the return passage 21; as shown in FIG. The distal end of the pressure-responsive valve 22 is formed to be able to fit into the return passage 21, and the distal end of the pressure-responsive valve 22 is configured to cut off communication between the return passage 21 and the suction chamber 13 by fitting into the return passage 21. ing.

The first pressure-responsive valve 22 is biased by the spring 24 in the direction of opening the return passage 21, but since the pressure within the working chamber 12 acts on the front end surface of the first pressure-responsive valve 22 in the valve-opening direction, The spring 24 may be omitted.

A first pressure adjustment valve 22 is provided on the rear end surface of the seventh housing 60.
9 i'l in the direction of closing the return passage 21 against
y) A rounded amount of pressure supply passage 8 that applies pressure!
l is formed. As shown in FIG. 2, one end 25A of the four pressure supply passage 25 in this example
3, the other end 25B is the suction chamber 11.
It opens at 1. And then, the pressure supply aisle 2
An intermediate pressure 1i 126 is located in the middle of the chamber, and in the middle of the pressure supply passage 25 between the intermediate pressure 1126 and the suction 1113, a pressure adjustment is made according to changes in the suction pressure in the suction chamber 13. , a second pressure-responsive valve 2 that opens and closes the pressure supply passage 2s.
7 is provided.

This intermediate royal 26 has a rotation 8, a front housing 5, a front night plate 3, a front housing 5, a front housing 7, and an axis MWI position 10.
This intermediate pressure chamber 26 is connected to each operation *12 through the sliding space between the rotor 7 and the front side plate 3, and when the compressor is rotating, the intermediate pressure chamber 26 is Inside the pressure chamber 26, the discharge pressure and suction pressure of the compressor are
When the compressor is stopped, the pressure becomes intermediate pressure chamber 2.
The pressure inside 6 is the same as the suction pressure. This is confirmed by experiment11-
It's broken. 9. To explain in detail about the second pressure-responsive valve 27, as shown in FIG. A pepphram 3° is attached to one end of the p1 plunger 29. A valve housing 81 is attached to the front surface of the front housing 5, and a space formed between the valve body 31 and the front housing 5 is opened to the atmosphere [32] and a suction pressure introduction 133 by the pet flam 30. has been completed.

Velofram 3o is introduced under suction pressure 11 into the atmosphere open chamber 32.
A spring 34 is installed to bias 33@, and suction pressure is introduced! 33 is a communication hole 21 formed in the housing 5 of 707.
5 (see diagram 3112), it is constantly in communication with the suction chamber 13. Therefore, when the load due to the suction pressure in the suction chamber 13 becomes larger than the set load of the spring 34, the ram 30 moves against the spring 34 to open to the atmosphere,
As a result, the granger 29% moves to the left in FIG. 1 and still contacts the valve housing 31.

The communication path (outer circumference #1I here) of the silane gloss 29 of the wi2 pressure-responsive valve 27 is! Shinsha 29 is spring 34
So when #I6 is being pushed to the right in the diagram, /4 Iro,
It is positioned and formed so as to conduct the pressure supply passage 2g.

Next, the operation of the rotary compressor having the above-mentioned configuration will be explained when it is applied to an automobile cooler system. In this case, the rotating shaft 8
receives the rotational driving force of the engine via an electromagnetic clutch (not shown). Nine, the suction port 14 is connected to the refrigerant evaporator of the cooler system, and the discharge port 20 is connected to the condenser of the cooler system.

When the rotor 7 rotates counterclockwise in FIG. 3, the refrigerant at the suction pressure is sucked from the evaporator side ($-)14. Operation ml through suction M1B and suction port 15! sucked inside.

If the capacity adjustment is not carried out, the return passage 21 is closed and the discharge capacity of the compressor is confined within the operating range 1!12 when the vane 11 moves to the position O shown by the broken line in FIG. In terms of the amount of refrigerant, the volume of the automatic actuation 1112 is the maximum.

On the other hand, when the capacity can be adjusted, the return passage 21 is opened and communicated with the suction 1113. Therefore, the discharge capacity of the compressor in this case is determined by the working chamber volume immediately after the rear vane 11 in the rotational direction of the two vanes 11 defining the working chamber 12 passes through the return passage 21. In this example, the position and size of the return passage 21 are set so that the volume at full capacity is about SOs, which is the maximum volume. The reduction rate is 5o
It may be a value other than 16.

If the pressure applied to the suction pressure introduction ii end face of the p472mm 30, that is, the load due to the suction pressure, is smaller than the set load of the spring 34, then II (for example, when the suction pressure is less than 2Y/as"G) will be Since the silant gloss 29 is pushed to the right in FIG. 1 by the spring 34, the suction pressure
It communicates with Therefore, the pressure acting on the back surface of the first pressure-responsive valve 22 becomes suction pressure, and the first pressure-responsive valve 22 is pushed to the left in FIG. Open 21. Then, the pressure fI
The I1 machine operates at a maximum volume of approximately son volume.

On the other hand, when the suction pressure to the suction chamber 13 is high tb and overcomes the spring load of the spring 34 of the second pressure-responsive valve 27, the grand gloss 29
is pushed to the left in FIG. Therefore, the inside of the intermediate pressure chamber 26 becomes an intermediate pressure between the discharge pressure and the suction pressure of the compressor, and this intermediate pressure
It acts on the back surface of the first pressure-responsive valve 22 via s. Ninth, the first pressure-responsive valve 22 moves to the right in FIG. Cut off communication. After all, the compressor has a maximum capacity of 1001! In this way, the % suction pressure is the set pressure (here 101G at 2 o'clock).
) When the pressure is too high, the return passage 21 is closed and the compressor operates at maximum capacity.

Trench 9, when the suction pressure drops below the set pressure, the return passage 21
is opened and the compressor shifts to operation at approximately 5091 capacity.

Here, regarding the movement of the compressor, Fig. 6 (a)
To explain with reference to = (b) - (c), for example, when the heat load decreases over time as shown in Figure 5 (&), in the case of a compressor that does not perform capacity adjustment, Figure 5 (b) )
As shown by the broken line, the suction pressure decreases as the heat load decreases. However, in the case of the variable capacity compressor according to the present invention, when the suction pressure decreases, the discharge capacity of the compressor decreases, and the suction pressure is thereby restored. As shown by the solid line, the suction pressure can be kept almost constant.

That is, the apparent discharge capacity of the compressor is continuously changed from 100 to 50 as shown in Figure 1I45 (c) to keep the suction pressure constant.

This is shown in Figure 6 (a), (b), (c).
As shown in (d), this is achieved by continuously changing the duty ratio of opening and closing of the return passage 21. In other words, when the heat load of the cooler system is high and the suction pressure is higher than the set pressure (the first (before point A in Figure 5 (a)), the compressor is always at 100% capacity 2 as shown in Figure 6 (a) K.
However, when the heat load decreases and the suction pressure falls below the set pressure (near point B in Fig. 5(e)), the return passage 21 opens and the compressor operates at a rate of about 50%. It becomes capacity operation. However, in this state, as soon as the capacity reaches 50'j, the suction pressure recovers above the set pressure and the return passage 21
As a whole, as shown in FIG. 6, the discharge capacity is often 100, and the apparent discharge capacity of this rounding compressor does not decrease much.

After that, when the heat load further decreases (near the 0 point in Figure 5 (o)), 50-hour capacity operation begins and the time required for the suction pressure to recover to the set pressure or higher after death is shown in Figure 6 (c). As shown in , the apparent discharge capacity of the compressor gradually decreases over time. Then, when the suction pressure decreases to around point D in Figure t#IJ5 (e), the compressor always operates at 50-capacity.Furthermore, the heat load is noticeably small, despite the 50-capacity operation. If the suction pressure drops, turn off the electromagnetic clutch and stop the operation of the pressure machine. When the compressor stops operating, the suction pressure increases, and therefore, when the compressor is restarted next time, an intermediate pressure will be applied to the back of the first pressure-responsive valve 22, but the intermediate pressure will be maintained for a short time after the compressor is stopped. Even if intermediate pressure is added in this way, the duty ratio of opening and closing of the #11 pressure-responsive valve 22 and the return passage 21 will change not only due to changes in heat load but also due to changes in engine speed. will also change automatically. In this case, the stability of the suction pressure depends on the quick response of the return passage 21, but in the present invention, the suction pressure and the intermediate pressure are selectively applied to the back surface of the first pressure-responsive valve 22, so the response is good.
According to the experiments conducted by the inventors,
The apparent trough of the compressor! In the I range (M to D in FIG. 5(c)), the return passage 21
was confirmed to open and close. Friend, in the present invention, as described above, intermediate pressure is applied to the back surface of the first pressure-responsive valve 22, and excessive pressure such as discharge pressure is not applied.
Even if the first pressure-responsive valve 22 repeatedly opens and closes the return passage 21, the first pressure-responsive valve 22 and the side plate 3 will not be damaged.

First, when the compressor operation is stopped, the suction pressure of the compressor increases, so the plunger 29 is pushed to the left in FIG. 1 and opens the pressure supply passage 26, but the intermediate pressure! 2
The pressure inside the pressure supply passage 25 decreases to a pressure equal to the suction pressure due to leakage to the suction equipment.
The first pressure-responsive valve 22 is separated from the return passage 21 to open the return passage 21. Therefore, when the compressor is started (1llK), the return passage 21 is open), and the compressor is started with a capacity of about 50 vI as shown in Fig. 5(e), so the electromagnetic clutch cannot be started. K so that the load can be reduced.

The above embodiments have been described above, but the present invention is not limited to the above embodiments. For example, the first pressure adjustment valve may be provided movably in the direction intersecting the return path. Good too. In this case, the pressure in the working chamber no longer acts on the first pressure-responsive valve in the valve-opening direction, so the spring can be used to bias it in the valve-opening direction. /1 aspect may be sufficient.

As described above, since the present invention changes the discharge capacity of the rotary compressor in accordance with changes in the suction pressure of the rotary compressor, the operation and control of the rotary compressor for adjusting the discharge amount is more efficient than in the past.
The number of stops can be significantly reduced.

Therefore, when a rotary compressor is applied to an automotive tara system, it will be possible to significantly reduce the number of times the electromagnetic clutch that connects the rotary compressor and the engine output side is turned on and off. It becomes possible to improve the driving feeling and cooling feeling of the car.

However, 4, the compressor capacity at startup can be reduced, the startup load can be reduced, and the electromagnetic clutch can be downsized.

Nine, because the number of times the electromagnetic clutch turns on and off decreases,
The durability of the two electromagnets is improved.

Furthermore, according to the present invention v4, it is possible to change the capacity continuously and with good responsiveness without using a solenoid valve other than a pressure-responsive valve, so the structure is simple, the number of parts is reduced, and it is safe. This means that it can be provided to @.

[Brief explanation of the drawing]

FIG. 1 shows an embodiment of the present invention, and 1-1 in FIG.
Figure 2 is a cross-sectional view along River I in Figure 1, Figure #13 is a view of the death site along Cao-men in Figure 1,
FIG. 4 is an enlarged sectional view of the vicinity of the first pressure-responsive valve and the second pressure-responsive valve. Figure 5 ta), (b), (e) and Figure 6 (a)
-(b), (c), and (d) are respectively explanatory views of the operation of the present invention. DESCRIPTION OF SYMBOLS 1... Compressor main body, 7... Rotor, 12... Working chamber, 13... Suction chamber, 17... Discharge chamber, 21...
Compressed fluid return passage, 22...first pressure responsive valve, 25
----Iro, G pressure supply passage, 26... intermediate pressure chamber,
27...Second pressure responsive valve. Figure 4 13 Figure 51 (Q) Time

Claims (1)

[Claims] 1. In the compressor main body, there is an operating chamber that repeatedly changes volume while moving with the rotation of the rotor, a suction chamber that enters the volume increase stage and is communicated with nine operating mK, and enters the minimum volume stage. In a nine-rotary compressor, the compressor body is formed with a discharge chamber that communicates with nine working chambers, and a compressed fluid return passage that communicates between the working chamber that has entered the one volume reduction stage in the compressor body and the suction chamber; A first pressure responsive valve that opens and closes the compressed fluid return passage; and a direction 1 that causes the first pressure responsive valve to close the compressed fluid return passage.
11. In the middle of the -f pressure supply passages, a pressure supply passage for applying pressure to the suction chamber is provided. A second pressure-responsive valve is provided to open and close the lower pilot pressure supply passage, and the lower pilot pressure supply passage communicates with the working chamber of the compressor through a small gap. A rotary compressor characterized in that during one rotation, the pressure in the pressure supply passage becomes intermediate between the discharge pressure and the suction pressure, and when the rotation is stopped, the pressure becomes the same as the suction pressure.