JPS6053692A - Coolant compressor - Google Patents

Abstract

PURPOSE:To make it possible to carry out various modes of operation with the control of a single control valve and as well to relieve shock upon starting, by disposing the control valve in the intermediate section of a coolant suction passage communicated with a compression chamber, and as well by piercing a coolant passage hole through a coolant passage and a rotor. CONSTITUTION:A coolant passage is branched out into an upper suction passage 6 and a lower suction passage 7 at a branch point 5 downstream of a suction passage opening 4. A control valve 8 disposed at the branch point 5, is rotationally driven and positioned by a control motor 10 through a shaft seal device 9. With this arrangement upon starting the control valve 8 gradually rotates from its fully close position at suction passages 6, 7 so that shock upon starting is reduced. Further, upon fully open operation the control valve 8 opens the suction passages with no resistance so that operation may be made exhibiting its maximum capability. Further, upon control operation the supply amount of coolant is regulated in accordance with the rotation of the control valve 8 to carry out capacity control operation so that it is possible to carry out energy saving operation. Upon resting the control valve 8 rotates at once to the position where the suction passages are fully closed to prevent high pressure gas and oil from counterflowing toward the evaporator side, thereby heat loss upon restarting is prevented.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a refrigerant compressor used in automobile cooling systems and the like.

The structure of the conventional example and its problems The conventional refrigerant compressor is
The refrigerant once entered the suction chamber 1, and then flowed into the compression section through the individual suction passages 2a and 2b communicating with the suction chamber 1. Furthermore, for the lubrication of the compression section, it has been common practice to supply refrigerating machine oil using a differential pressure method from an oil reservoir 3a provided at the rear of the compressor.

In such a configuration, when the compressor is stopped after operation, the refrigerating machine oil in the oil sump 3a flows out from the oil supply passage 3b into the compression section when the differential pressure disappears.

Furthermore, there is a drawback that the high-temperature refrigerating machine oil or refrigerant gas dissolved therein flows backward through the suction passages 2a and 2b from the compression section to the evaporator of the refrigeration cycle, and warms the evaporator. Was.

On the other hand, the refrigerant compressor used for automobile air conditioning is directly driven by the engine via a belt, so when the engine rotates at high speed, the compressor's refrigeration capacity is surplus, and the discharge pressure and temperature on the refrigeration cycle are low. Various financial harms will occur, such as excessive amounts. For this reason, control devices such as EPR are often used in recent years, but they often have drawbacks such as being expensive and having poor refrigeration cycle efficiency. In addition, control by attaching and detaching an electromagnetic clutch is currently the mainstream, and it has disadvantages such as noise during attaching and detaching, shock at startup, and changes in the temperature of the blown air, which impair the feeling of operation and temperature control.

Purpose of the Invention The purpose of this invention is to prevent the backflow of high temperature gas and oil to the evaporator side after the operation is stopped, and to prevent the compressor from freezing when there is excess refrigerating capacity, such as during high speed rotation or when the heat load inside the vehicle is small. It is an object of the present invention to provide a refrigerant compressor which is capable of performing so-called capacity control operation in which the capacity is controlled, and which can alleviate startup shock at the beginning of operation Ui1.

Structure of the Invention The refrigerant compressor of the present invention has a refrigerant suction passage communicating with a compression chamber and a refrigerant circulation hole formed through a rotating body, and is disposed in the middle of the refrigerant suction passage. It is equipped with a control valve that controls the supply amount and a control motor that rotationally drives this control valve.By controlling the rotation of one control valve, various modes of operation shown below are possible. It has great and unique effects.

(1) At startup, the control valve rotates gradually from the suction passage fully closed position to open the suction passage, so there is no sudden compression and there is less startup shock9.
Does not impair driving feeling.

(2) During full-time operation, the control valve opens the suction passage without flow path resistance, and the compressor operates to its maximum capacity.

(3) During control operation When the cooling heat load is small, the refrigerant supply amount is adjusted by rotating the ff1lJ control valve to perform capacity control operation that suppresses the refrigerating capacity, resulting in energy-saving operation that reduces power consumption. I can do it.

(4) When stopped When the compressor is stopped after operation, the control valve immediately rotates to the position that fully closes the suction passage, and prevents high-temperature gas and oil from flowing back into the evaporator. There is no discomfort caused by a sudden rise in temperature, and heat loss during restart can be prevented.

DESCRIPTION OF THE EMBODIMENTS An embodiment of the present invention will be described with reference to FIGS. 2 to 6. FIG. 2 shows a longitudinal sectional view of the refrigerant compressor in this embodiment. In the figure, reference numeral 4 denotes the inlet of the suction passage, and the upper suction passage 6. The passage branches into a lower suction passage 7. A rotatable control valve 8 is inserted into the branch point 5, and a rotatable control valve 8 is inserted into the iH control valve 8 via a shaft sealing device 9.
At 10 pm, the rotary drive 2 was positioned.

FIG. 3 is a detailed view of the control valve 8. FIG. 3(a) is a 1,000-sided view, and FIG. 3(b) is a front view. This control valve 8 has a cylindrical shape, and there are a passage on the circumference that has penetrating entrances and exits 11, 3.2, a passage that grows an inlet 013 that does not pass through, and a passage that has an outlet 14 that does not pass through in the axial direction. This is a rotary switching valve.

Next, the operation of this control valve 8 will be explained with reference to Figures 4 to 6. .

In FIG. 4, since the control valve 8 has one coil inlet and one outlet and one coil 12 at the top and bottom, the refrigerant gas flows into both the soil suction passage 6 and the lower suction passage 7.

In Figure 5 - cPi, since the inlet 13 of the control valve 8 faces in the ± direction, the refrigerant gas that has flowed in from the inlet 13 flows through the outlet 14 into the salmon 1 upper suction passage 6 and does not flow into the Shimohanjin passage 7. . At this time, the compressor has only about R5 refrigerating capacity, and since it is a capacity control compressor, the required power is reduced.

In FIG. 6, the suction passage artificial part 4 does not communicate with any of the suction passages 6 and 7, and the passage is completely blocked. Gas inflow and outflow is prevented.

Finally, we will explain how to use the above-mentioned Ka14JJ mote.

The compressor is running! When the control valve 8 is not closed, the control valve 8 is in the position shown in Fig. 6 (/r≧closed mode 1'), and when the compressor starts operating, the control valve 8 gradually rotates 90 degrees and closes the intake passageway. 4 is made into a U sound hole, the refrigerant circulation rate increases slowly, and the final 8 Perform rapid cooling.

Next, when the air conditioner reaches the set temperature, 'υ1j control valve 8
The compressor rotates to the state shown in FIG. 5 (control mode), and the compressor enters the control operating state. At this time, the required power is reduced because the pressure balance state of the refrigeration cycle changes and the amount of refrigerant circulated is halved, resulting in power savings.

After this, full throttle mode and '! +! Capacity f when the electromagnetic clutch is not engaged or disengaged due to repeated operation in X-open mode
&il #Able to drive.

When stopping the operation of the compressor, the control valve 8 is immediately rotated from the fully open mode or control mode position to the fully closed mode position shown in FIG. 7 and suction passage inlet 4 [because they are no longer in communication,
When the compressor is stopped, oil accumulates in the compressor sump 15/L.
- Even if refrigerating machine oil flows out from the supply passage 16 into the pressure m section and further flows backward through the first suction passages 6 and 7, it does not enter the evaporator side housing of the refrigeration cycle.

Therefore, according to this embodiment, a control valve 8 capable of switching the flow passage by rotation is inserted into the branch point of the two branched suction passages 6 and 7, and the control valve 8 is controlled by the control motor IO. Since the rotary drive is used for one positioning, the following effects can be obtained.

(1) By gradually increasing the refrigerant flow rate at startup, the startup shock can be alleviated, a smooth load torque curve can be obtained, and the driving feeling is not impaired.

(2) The compressor operation can be switched between 100% and 50% of the compressor's refrigeration capacity according to the heat load of the vehicle, allowing for capacity control operation throughout the year. In addition to reducing fuel consumption, there is no need to worry about noise caused by attaching and disengaging the electromagnetic clutch, and the driving feeling is not impaired by the start-up shock.

(3) When the compressor is stopped, by immediately tracing and closing the suction passage, the backflow of high-temperature scum and oil to the evaporator side due to the flow of refrigerating machine oil from the compression part from the lubrication path is prevented. ,
Since the evaporator is not heated, thermal loss caused by turning the compressor on and off can be reduced, improving economic efficiency. Furthermore, the practical effects are great, such as the comfort level being improved because the m-tone feeling is not impaired due to the rise in the temperature of the blown air due to the rise in the temperature of the evaporator.

Effects of the Invention The refrigerant compressor of the present invention can prevent the backflow of high temperature gas and oil to the evaporator side after tJ and operation stop. The effect of alleviating the startup shock cannot be obtained.

[Brief explanation of drawings]

FIG. 1 is a vertical cross-sectional view of a conventional refrigerant compressor, FIG. 2 is a vertical cross-sectional view of a refrigerant compressor according to an embodiment of the present invention, and FIG.
a) and (b) are the plan view and front view of the flilJ# valve, respectively, and Figures 4 to 6 are! It is an operation mode diagram of the II control valve. 4. Inhalation passage artificial part, 5. Branch point, 6. Lower suction passage,
7...1 suction passage, 8...control valve, 1o...control motor 1st drawing 16 Figure 2 (a) (b) Figure 3 Figure 4 Figure 5 Figure 6

Claims (2)

[Claims] (1) A refrigerant suction passage communicating with the compression chamber, and a control valve having a refrigerant flow hole formed through a rotating body and disposed in the middle of the refrigerant suction passage and controlling the amount of refrigerant supplied by its rotation. , and a control motor that rotationally drives the control valve. (2) The refrigerant suction passage branches into a plurality of parts along the way, the control valve forms a plurality of combinations of refrigerant flow holes and is disposed at a branch point of the refrigerant suction passage, and the control motor rotates the control valve. A refrigerant compressor according to claim 1, which controls the number of branch passages opened in the refrigerant suction passage.