JPS63162980A - Compressor - Google Patents

Abstract

PURPOSE:To lower the average temperature of a compressing mechanism section and continuously deprive the compressed gas of heat by providing a cooling mechanism heat-exchanging with the compressed gas in a compression chamber on the compressing mechanism section. CONSTITUTION:When a compressor is operated, the pressure and temperature in a compression chamber 13 gradually rise, thereby the temperature of the end plate 18a of a stationary scroll rises. The refrigerant sealed in a pipe 20 and a passage 19 is gradually gasified while absorbing heat from the end plate 18a as the temperature of the end plate 18a rises, and it reaches a radiating section 21 at the outside of an enclosed casing 1 via the pipe. Here the refrigerant radiates heat, and is liquefied and again returned to the passage 19 via the pipe 20. Subsequently this cycle is repeated, thereby the temperature of the refrigerant gas in the compression chamber 13 is lowered.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a compressor used in a refrigeration cycle or the like, and particularly relates to improving the efficiency of a refrigeration cycle.

2. Description of the Related Art Conventional components will be explained with reference to FIGS. 4, 5, and 6. 1
2 is a sealed casing, 2 is an electric motor section, and a block 3 is placed above it. Fixed scroll 4. A compression mechanism section 7 composed of an orbiting scroll 6 and an anti-rotation mechanism 6 is fixed. The fixed scroll 4 is formed of an end plate 4a and an involute standing upright on the end plate 4a, or a curve similar to an involute, and has a wrap 4b having a uniform thickness and height.
It has a multi-layer structure and is fixed to the block 3 with a mirror plate 4a. The orbiting scroll 5 is constituted by an end plate 6a and a wrap 6b that stands upright on the end plate 6a and has the same curve as the wrap 4b of the fixed scroll 4, and is restrained by an anti-rotation mechanism 6 called an Oldham mechanism. The fixed scroll 4 and the orbiting scroll 6 each have a wrap 4b, 5
The winding end ends 4 b' and 5 b' of b are aligned with each other with a certain angle shifted from each other. , 8 is a discharge hole, and 9 is a suction hole.The discharge hole 8 is provided at the center of the involute of the fixed scroll 4, and the suction hole 9 is provided so as to intersect with the winding end portion 4c of the involute of the fixed scroll 4. Hole 9 communicates with suction chamber 9a. 1o is a protrusion provided on the orbiting scroll 6 with a surface trap on the side opposite to the wrap 5b, and is concentric with the center of the involute of the lug 6b. Reference numeral 11 denotes a shaft supported by the block 3, and the stain motive section 2 is installed by housing the protrusion 1o of the orbiting scroll 6 in a boss section 11a provided at the end on the compression mechanism section 7 side and eccentric from the center of the shaft.
and the orbiting scroll 5 are connected. Further, reference numeral 11b denotes an oil supply passage, which communicates the boss portion 11a with the lower part of the sealed casing 1.

Reference numeral 12 denotes a space formed on the back surface of the orbiting scroll 5, and communicates with the suction chamber 9a via a clearance A between the mirror surfaces 4a and 5a. Reference numeral 13 denotes a compression draft 14 that is a thrust holding mechanism (for example, a ball bearing, etc.) that comes into contact with the end plate 6a of the orbiting scroll 6 on the side opposite to the lap. 15 is a suction pipe communicating with the suction hole 9, and 16 is a discharge pipe. Further, a check valve mechanism 17 formed by a valve 17a and a spring 17b is housed in the suction hole 9.

Next, the compression mechanism of the scroll compressor will be explained.

The rotational movement of the shaft 11 accompanying the rotation of the electric motor section 2 is transmitted to the orbiting scroll 6 via the boss section 11a and the projection section 10, but due to the action of the rotation prevention mechanism 6, the orbiting scroll 6 does not rotate on its own axis. The fixed scroll 4 rotates around the involute center as the rotation center. At this time,
Winding end 5b' of the wrap 5b of the rotating spool 5
is the wrap 4b of the fixed scroll 4, and the fixed scroll 4
The winding end 4b' of the wrap 4b is the orbiting scroll 5
Inhalation is complete when the wraps 5b are in contact with each other, and as the two contact points of the wraps 4b and 5b approach the center of the involute as the orbiting scroll 6 revolves, the pressure in the compression space 13 increases. do.

In the compression mechanism of this scroll compressor, the pressure in the suction chamber 9a is lower than the pressure in the suction pipe 16, and the force due to the differential pressure is greater than the spring force of the spring 17b pushing up the valve 17a. When the check valve mechanism 17 is in the open state, the refrigerant is sucked through the suction pipe 16, the suction hole 9°, and the suction chamber 9a. The sucked refrigerant is compressed and discharged into the -H sealed casing 1 through the discharge hole 8, and then discharged through the discharge pipe 16 to a cooling system (not shown).

Problems to be Solved by the Invention In such a conventional groove bottom, the compression state is shown on a Mollier diagram as shown in FIG. 6. That is, on the Mollier diagram,
Pl: Low pressure, P2: High pressure, tl: Compressor suction temperature, t2: Average temperature of the compression mechanism, t3: Discharge gas temperature, 11: Enthalpy of suction gas, i3: Inthalbi of discharge gas, i4: Assuming the enthalpy of the discharged gas during adiabatic compression, the compressor has a low pressure P1 and a suction temperature t1.
Compression is started in state (■), and compression is carried out to state (2) with high pressure P2 and discharge temperature t3.The power required for compression is equivalent to the enthalpy difference (i3-il). be. By the way, compressed gas is completely insulated during compression. In other words, in the case of theoretical adiabatic compression, the compressor compresses from the state (■) of low pressure P1 and suction temperature t1 to the state (4) (■) of high pressure P2 and discharge temperature. i4-il). Therefore, in actual compression, an extra power equivalent to (13-14) is required compared to the theoretical adiabatic compression.

The cause of this is ■ Heat reception of the gas during the suction stroke @ Heat reception of the gas during the compression stroke (Heat reception in the section ■ → ■ where the temperature is lower than the average temperature t2 of the compression mechanism in the Mollier diagram) θ Low pressure side of the compressed gas This is because the pressure and temperature of the gas in the compression chamber increase due to leakage, etc. Among these, it is possible to improve the leakage of θ to some extent by reducing the clearance.

However, concrete measures have been taken to reduce heat reception, such as cooling the compressor mechanism indirectly by fan cooling or natural cooling of the hermetic casing, or cooling the compressed gas by liquid injection. However, for the former, it is less effective in cooling the compression mechanism, especially the surfaces that come into contact with the compressed gas, and for the latter, the amount of liquid refrigerant injected must be increased in order to provide sufficient cooling capacity. This resulted in problems such as an increase in input and a decrease in efficiency.

The present invention solves the problems of the conventional example described above.
It eliminates loss due to heat reception and further takes heat from the compressed gas, lowering the power to more than the adiabatic compression power.

Means for Solving the Problems According to the present invention, a cooling mechanism for exchanging heat with compressed gas is provided in a compression mechanism section constituting a compression chamber.

Effects The present invention has the above-described configuration, and by lowering the average temperature of the compression mechanism and continuously removing heat from the compressed gas, it not only eliminates loss due to heat reception and approaches adiabatic compression power, but also The compression power is less than the adiabatic compression power, and has the effect of improving efficiency and reliability by cooling the compressor.

EXAMPLE An example of the present invention will be described below with reference to FIGS. 1, 2, and 3. Incidentally, the same parts as in the conventional example are given the same reference numerals, and the description thereof will be omitted. Reference numeral 18 is a fixed scroll, which has an end plate 18a and a wrap 18b as in the conventional case. Further, a passage 19 is provided in the end plate 18a of the fixed Shumir. 20 is a pipe having a heat radiation part 21 on the outside of the sealed casing 1, and both ends 20a and 20b are respectively connected to the passage 1.
By communicating with the ends 19a and 19b of 9, a cooling mechanism 22 consisting of a heat pipe is formed as a closed circuit. Moreover, a refrigerant is sealed within this closed circuit.

Note that in the figure, * indicates a liquid refrigerant, and arrows indicate the flow direction of the refrigerant.

In the above configuration, when the compressor is operated, the pressure and temperature of the compression chamber 13 gradually rise as in the conventional case, but this causes the temperature of the end plate 18a of the fixed scroll to rise.

The refrigerant sealed in the pipe 20 and the passage 19 remains in the passage 1e as a liquid refrigerant before operation, but as the temperature of the head plate 18a increases, it gradually vaporizes while absorbing heat from the head plate 18a and flows through the pipe. and reaches the heat radiating part 21 outside the sealed casing 1. Here, the refrigerant radiates heat and liquefies, and returns to the passage 19 again via the pipe 2o. By repeating this cycle thereafter, the passage 19 acts as a heat absorbing part of the heat pipe type cooling mechanism, lowering the temperature of the end plate 18a of the fixed scroll, and finally lowering the temperature of the refrigerant gas in the compression chamber 13. It happens. Here, if the capacity of this heat pipe type cooling mechanism is sufficiently large), and the boiling point of the refrigerant in the heat pipe is the suction gas temperature t.

If the following is selected, the temperature t2 of the end plate 18a can be lowered to near the suction gas temperature t, and therefore the compression chamber 13
The compressed gas inside the compressor does not receive heat; on the contrary, heat is removed during one compression stroke. That is, on the Mollier diagram, the state when continuous heat removal is performed is t; discharge gas temperature, t6;
If the average temperature of the compression mechanism is i5; the enthalpy of the discharged gas, then the compression power in the case of theoretical adiabatic compression (x 4
-11) Compression can be performed with less power by (14-16).

That is, compared to the conventional compression power (i - i ), (1s - t s
), it is possible to reduce the input power, significantly improving efficiency, and improving the reliability of the compressor through cooling.

In this embodiment, the heat absorbing part is provided in the end plate of the fixed scroll, but it goes without saying that it may be located anywhere as long as it can efficiently remove heat from the gas in the compression chamber.

In addition, although this embodiment has been explained using a scroll type compressor, it goes without saying that similar effects can be obtained with other rolling piston type Palm 7 Pro type compressors and compressors with other compression methods. The structure may be configured so that the ambient temperature of the refrigerant is lowered and heat is constantly removed from the refrigerant in the compression chamber.

Although a heat pipe type cooling mechanism has been described, it goes without saying that other cooling methods may be used as long as they require less power.

Effects of the Invention As is clear from the above description, the present invention includes an electric motor section, a compression mechanism section connected to the electric motor section, and a compression chamber formed by the compression mechanism section. Since it is equipped with a cooling mechanism that exchanges heat with the compressed gas, efficiency can be improved by significantly reducing compression power, and cooling improves the reliability of the compressor.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of a scroll compressor showing an embodiment of the present invention, Fig. 2 is a sectional view taken along the line ■-■' in Fig. 1, and Fig. 3 shows the compression power of the present invention. Mollier diagram showing,
FIG. 4 is a longitudinal sectional view of a conventional scroll compressor, FIG. 6 is a sectional view taken along the line v-v' in FIG. 4, and FIG. 6 is a Mollier diagram showing the conventional compression power. 2... Electric motor section, 7... Compression mechanism section,
13... Compression chamber, 22... Cooling mechanism. Name of agent: Patent attorney Toshio Nakao and 1 other person22
-7'j Disposer groove Fig. 1 γ - Pressure distribution tx, side part Fig. 2 g? ? Figure 3 Enthalpy 4'Kinut''L3 Figure 4

Claims (2)

[Claims] (1) A cooling device that includes an electric motor section, a compression mechanism section connected to the electric motor section, and a compression chamber formed by the compression mechanism section, and that exchanges heat with the compressed gas in the compression chamber in the compression mechanism section. A compressor equipped with a mechanism. (2) The compressor according to claim 1, wherein the cooling mechanism is a heat pipe type cooling mechanism having a heat absorption section within the compression mechanism section.