KR100500492B1 - Self-contained regulating valve, and compression type refrigerating machine having the same - Google Patents

Abstract

The self-supporting regulating valve is provided with the spool 13 which moves axially in the internal space of the cylindrical valve main body 11. One pressure P ₁ acts on one end surface of the spool 13, and the other pressure P ₂ acts on the other end surface of the spool 13. The through hole 13a is provided in the spool 13. When the pressure difference between the one pressure P ₁ and the other pressure P ₂ exceeds the set value, the through hole 13a and the conduit 12 connected to the valve body 11 communicate with each other so that the self-standing valve is open. Becomes

Description

Self-contained regulating valve and compression freezer with it {SELF-CONTAINED REGULATING VALVE, AND COMPRESSION TYPE REFRIGERATING MACHINE HAVING THE SAME}

The present invention relates to a self-supporting regulating valve and a compressed refrigerator having the self-standing regulating valve.

9 is a system diagram showing a multistage compressed turbo-cooler according to the prior art. As shown in the figure, in the evaporator 1, the refrigerant liquid (e.g., organic refrigerant such as carbon fluoride) is heated with cold water (or brine) 3 flowing in the tube 2 to generate a refrigerant gas. . At this point, the cold water 3 is cooled by heat exchange in the evaporator 1 and then transferred to the outside.

The turbo-compressor 4 with two impellers sucks the refrigerant gas evaporated by the evaporator 1 and is compressed in two stages by a two-stage impeller rotated by an electric motor (not shown). Eject gas. The refrigerant gas from the intermediate cooler 5 is sucked into the impeller located in the second stage (intermediate stage). In the condenser 6, the hot, high pressure refrigerant gas discharged from the turbo-compressor 4 flows into the tube 7 and is cooled by the cooling water 8 to condense and liquefy. At this point, the cooling water 8 is heated by heat exchange in the condenser 6 and then discharged to the outside. The condensed refrigerant liquid accumulates at the bottom of the condenser 6.

The intermediate cooler 5 evaporates a portion of the refrigerant supplied from the condenser 6 and allows the final refrigerant gas to flow through the conduit 10 into the second stage of the turbo-compressor 4. The refrigerant gas is then compressed by a two stage impeller to increase latent heat. That is, in the intermediate cooler 5, the refrigerant liquid introduced from the condenser 6 is decompressed to the intermediate pressure by the one-stage orifice and expanded, and is partially converted into the refrigerant gas. As described above, the refrigerant gas flows into the two stage impeller of the turbo-compressor 4 (intermediate suction). On the other hand, the excess refrigerant liquid cooled by the evaporation of the refrigerant liquid is further depressurized by the two-stage orifice, and then flows into the evaporator 1. At the same time, the intermediate cooler 5 functions to maintain a constant pressure difference between the condenser 6 and the evaporator 1. For this purpose, the pipeline 10 is provided with an intermediate suction valve 9 to regulate the flow rate of the refrigerant gas supplied to the turbo-compressor 4 via the pipeline 10. Specifically, the internal pressure of the condenser (6) (P ₁₎ and to be detecting the pressure (P ₂₎ of the evaporator (1), a second pressure difference between two pressure (△ P) is the pressure when the condition exceeding the set point The switch is activated. As the pressure switch operates, the solenoid valve or the electric valve opens. On the other hand, the valve closes when the pressure difference is less than the set value. That is, the above-described intermediate suction valve 9 according to the prior art is composed of a valve in which a pressure switch, an electric valve and an electric valve are integrated.

In the turbo-freezer according to the prior art, a pressure switch and an electric valve or an electric valve are integrated as an intermediate suction valve 9 so that the pressure difference between the internal pressure of the evaporator 1 and the internal pressure of the condenser 6 is kept constant. Use Therefore, the intermediate suction valve 9 itself is enlarged and expensive. Thus, the price of a turbo-chiller is expensive.

Furthermore, in turbo-coolers, the flow rate of a fluid, such as a refrigerant, is generally adjusted according to the pressure difference between one pressure P ₁ and the other pressure P ₂ , ie ΔP (= P ₁ -P ₂ ). There is a case where there is a need, that is, a case other than the case described above.

The present invention is carried out in view of the above-described prior art, and an object of the present invention is to provide a low-cost simple structure that can open and close a valve through which a fluid such as a refrigerant flows according to a pressure difference between one pressure and the other pressure. It is to provide a self-supporting regulating valve to be used and a compressed refrigerator having this self-standing regulating valve.

1 is a structural diagram showing a self-supporting regulating valve according to a first embodiment of the present invention;

2 is a structural diagram showing a self-supporting regulating valve according to a second embodiment of the present invention;

3 is a structural diagram showing a self-supporting regulating valve according to a third embodiment of the present invention;

4 is a system diagram showing a turbo-cooler according to a fourth embodiment of the present invention;

5 is a system diagram showing a turbo-cooler according to a fifth embodiment of the present invention;

6 is a system diagram showing a turbo-cooler according to a sixth embodiment of the present invention;

7 is a system diagram showing a turbo-cooler according to a seventh embodiment of the present invention;

8 is a system diagram showing a turbo-cooler according to an eighth embodiment of the present invention, and

9 is a system diagram showing a multistage compressed turbo-cooler according to the prior art.

In order to achieve the above object, the first aspect of the present invention relates to one pressure transmission chamber, which is a space formed between a cylindrical valve body and one end surface of a spool formed to be axially movable in an internal space of the valve body. One of the introduced pressures acts on one side of the spool; The other pressure introduced into the other pressure transmission chamber, which is a space formed between the valve body and the other end surface of the spool, and the spring force of the preload spring act on the other end surface of the spool; When the through-hole is provided in the spool, and the pressure difference between one pressure and the other pressure exceeds the set value, the through hole and the pipe connected to the valve body communicate with each other so that the self-standing valve opens, while the pressure difference exceeds the set value. When not, the through hole and the conduit are self-standing valves configured to shut off such that the self-standing valve is closed.

According to the present invention, the valve can be opened and closed according to the pressure difference between one pressure and the other pressure. Thus, a cheap valve of a simple structure can be supplied.

In the second aspect of the present invention, one pressure introduced into one pressure transmission chamber, which is a space formed between the cylindrical valve body and the flange portion provided in the middle of the spool, acts on the flange portion of the spool; The other pressure introduced into the other pressure transmission chamber, which is a space formed between the valve body and the one end surface of the spool axially movable in the internal space of the valve body, acts on one end surface of the spool; The spool moves in response to the pressure difference between one pressure and the other pressure, so that the other end surface of the spool is a self-supporting regulating valve formed so as to close or open an area between the open ends of two conduits connected to the valve body.

According to the above invention, the valve is automatically opened and closed in accordance with the pressure difference between one pressure and the other pressure, similarly to the first invention. At this point, the area between the open ends of the two conduits connected to the valve body by the other end surface of the spool is opened and closed in accordance with the movement of the spool, so that the sealing property can be better maintained in the portion. Therefore, a cheap valve of simple structure with improved sealing property of the opening and closing portion can be supplied.

In the third aspect of the present invention, the fluid pressure controlled by the self-supporting regulating valve acts as one pressure on one end surface of the spool which is axially movable in the inner space of the cylindrical valve body; The other pressure flowing into the pressure transmission chamber, which is a space formed between the valve body and the other end surface of the spool, and the spring force of the preload spring act on the other end surface of the spool; When the through-hole is provided in the spool, and the pressure difference between one pressure and the other pressure exceeds the set value, the through hole and the pipe connected to the valve body communicate with each other so that the self-standing valve opens, while the pressure difference exceeds the set value. If not, the self-standing valve is configured to be closed so that the through-hole and the conduit are closed.

According to the present invention, the valve can be opened and closed automatically according to the pressure difference between one pressure and the other pressure which is the pressure of the fluid to be controlled. Thus, a cheaper valve of simpler structure can be supplied than the self-supporting regulating valve described in the first invention.

The fourth invention is a multi-stage compression type refrigerator having an intermediate cooler, wherein the self-standing regulating valve described in the first invention or the second invention is interposed in the middle of a pipeline returning the refrigerant from the intermediate cooler to the compressor; The internal pressure of the condenser acts as a pressure on the self-standing valve, and the internal pressure of the evaporator acts as the other pressure on the self-standing valve, and when the pressure difference between these two pressures exceeds the set value, the self-standing valve opens. It becomes a state.

According to the present invention, the pressure of the intermediate cooler can be automatically adjusted to an appropriate value by a low cost valve with a simple structure.

5th invention isolate | separates between the casing which accommodates the drive motor of a compressor, and a casing which accommodates a speed-up gear and an impeller by a partition, and provides a sealing means in the clearance gap between a partition and the rotating shaft which penetrates this partition. Compression with a compressor configured to prevent lubricating oil lubricating the gears from flowing into the casing of the drive motor, to introduce refrigerant gas into the casing of the drive motor, to cool each part of the drive motor, and to discharge the refrigerant gas from the casing. In the refrigerator, the independence adjustment valve described in any one of the first to the third invention is interposed in the middle of the pipeline for discharging the cooling refrigerant from the drive motor side casing, and the drive motor side casing is provided as one pressure to the independence adjustment valve. Internal pressure of the gearing casing acts as the other pressure to the self-standing valve. Operation and, when the pressure between the two pressure difference exceeds a set value, the self-standing control valve is in an open state.

According to the present invention, the internal pressure of the drive motor side casing can be automatically adjusted to an appropriate value by a low cost valve of a simple structure, and lubricating oil can be prevented from flowing from the gear chamber.

In a sixth aspect of the present invention, there is provided a compressor in which a refrigerant gas is introduced into a casing of a drive motor to cool each part of the drive motor, and then the refrigerant gas is discharged from the casing. The independence adjustment valve described in any one of the first to third inventions is interposed in the middle of the pressure equalizing pipe which equalizes the pressure at the coolant supply port side into which the cooling refrigerant is introduced and the pressure at the coolant discharge port at which the cooling refrigerant is discharged. The internal pressure at the refrigerant supply port side of the casing acts as one pressure on the regulating valve, and the internal pressure on the refrigerant outlet side of the casing acts as the other pressure on the self-standing regulating valve, and the pressure difference between the two pressures exceeds the set value. The self-standing valve is open.

According to the present invention, the pressure difference between the internal pressure at the coolant supply port side of the drive motor casing and the internal pressure at the coolant discharge port side of the casing can be adjusted automatically by the low cost valve of the simple structure, and fully exhibit the cooling effect of the cooling refrigerant. After this, the rotational load on the drive motor by the cooling refrigerant can be adjusted to an appropriate range.

A seventh invention is a compressed refrigerator having a compressor configured to store lubricating oil in a casing, and circulate the lubricating oil by means of an oil pump to lubricate the rotating part, wherein the lubricating oil described in the second invention is described in the middle of a pipeline from the condenser to the casing. When the self-standing valve is interposed, the internal pressure of the casing acts as one pressure on the self-standing valve, the hydraulic pressure of the lubricant acts as the other pressure, and the pressure difference between the two pressures is less than the set value. The self-standing valve is open.

In the present invention, when the oil pump stops due to a power failure, the lubricating oil supply by the oil pump is stopped, and the oil pressure of the oil pump, which is the other pressure, drops rapidly. Therefore, the internal pressure of the casing, that is, the pressure difference from one of the pressures, is less than the set value, thereby opening the self-supporting regulating valve. As a result, the liquid refrigerant in the condenser expands and enters the casing due to the stop of the refrigerator due to the power failure. The pressure acts on the head tank in the casing. The pressure of the refrigerant entering the head tank replaces the function of the oil pump and continuously supplies lubricant. Therefore, even if the supply of lubricating oil is cut off, lubricating oil can be continuously supplied to the rotating part which rotates continuously by an inertia force. Thus, problems such as seizure of the rotating part can be avoided.

An eighth invention includes a rotary compressor configured to rotatably support a rotating portion by a fluid bearing using a refrigerant liquid as a working fluid, and to condense a high temperature and high pressure refrigerant gas formed by compression of the compressor by a condenser. And a main refrigerant system configured to supply the evaporator to evaporate and return it to the compressor as refrigerant gas, a refrigerant tank for storing the refrigerant liquid, and a refrigerant pump. In a compression freezer comprising a main refrigerant system and a lubrication system, which are separately installed in a lubrication system configured to be introduced into and circulated therein, the conduit communicating with the liquid reservoir of the condenser and the conduit forming the lubrication system. In the middle of the self-standing adjustment valve described in any one of the first to third invention is interposed, When the internal pressure of the liquid reservoir acts as one pressure on the valve, and the internal pressure in the duct of the lubrication system acts as the other pressure on the valve, and when the pressure difference between these two pressures exceeds the set value, the self-standing adjustment The valve is open.

According to the present invention, the refrigerant liquid can be supplied from the liquid reservoir to the lubrication system via the self-standing regulating valve even if the refrigerant pump is out of power and the refrigerant liquid is not circulated in the refrigerant system. Therefore, problems such as sticking of the bearing can be avoided. Moreover, the above-mentioned effect can be produced by a cheap valve of simple structure.

<1st embodiment>

1 is a structural diagram showing a self-supporting regulating valve according to a first embodiment of the present invention. As shown in the figure, an inlet port 11a and an outlet port 11b for inflow and outflow of fluid are formed opposite the central portion of the valve body 11 of the self-supporting regulating valve I forming a cylindrical closed space. The spool 13 is accommodated in the inner space. The self-supporting regulating valve I is connected to the conduit 12 located up and down in the figure through the inlet 11a and the outlet 11b. The spool 13 has a through hole 13a disposed in the inlet port 11a and the outlet port 11b and used as a fluid passage, and in the left and right directions in the figure along the axial direction in the internal space of the control valve 11. It is possible to slide. A predetermined preload is applied to one end surface of the spool 13 by the preload spring 14. O-rings 15 and 16 are fitted to the outer circumferential surface at the left and right ends of the spool 13 to form two spaces between each end face of the spool 13 and each end face inside the valve body 11. . Each of the above spaces is used as the pressure transmission chambers 17 and 18, and the pressure transmission chambers have one pressure (through the pressure introduction holes 11c and 11d formed in the pressure transmission pipes 19 and 20 and the valve body 11). P ₁ ) and the other pressure P ₂ . In Figure 1, then the pressure difference (△ P) between at least one set point pressure (P ₁₎ and the other of the pressure (P ₂₎ shows an open type wherein the self adjusting valve (Ⅰ). At this time, the left end surface of the spool 13 is in contact with the stopper 22 to define its position. On the contrary, when the differential pressure DELTA P decreases, the spool 13 moves to the right side of the drawing in accordance with the reduced amount, and when the right end surface is in contact with the stopper 21, the spool 13 is stopped. The location is limited. As described above, at the time when the spool 13 is in contact with the stopper 21, the self-supporting regulating valve I is in a fully closed form. When the spool 13 comes into contact with the stopper 22, the self-supporting regulating valve I is in a fully open state.

<2nd embodiment>

2 is a structural diagram showing a self-supporting regulating valve according to a second embodiment of the present invention. As shown in the figure, the self-supporting regulating valve II is a flange portion 113a provided in a central portion penetrating through the one pressure transmission chamber 117, the space between the tubular valve body 111, and the spool 113. ) Is configured such that one pressure P ₁ introduced into N) acts on the flange portion 113a. The spool 113 may be moved in the axial direction in the internal space of the valve body 111. The other pressure transmission chamber 118 is a space formed between the valve body 111 and one end surface of the spool 113. The other pressure P ₂ acts on one end surface of the spool 113. The preload spring 114 is fitted into a portion of the spool 113 facing the pressure transfer chamber 117 to continuously press the spool 113 to the left of the figure. Therefore, in the normal state, the spool 113 is moved to the left side of the drawing by the spring force of the preload spring 114 (the position of the spool 113 is indicated by the solid line in the drawing). When the other pressure P ₂ is greater than the combined force of one pressure P ₁ and the spring force of the preload spring 114, the spool 113 moves to the right in the drawing.

The conduit 112 is connected to the inlet 111a and the outlet 111b provided in the valve body 111. As a result, the region between the inlet 111a and the outlet 111b is closed, the spool 113 is in contact with the right stopper 121 in the drawing, and the region between the conduits 112 is closed. When the spool 113 is in contact with the left stopper 122 in the figure, the region between the inlet 111a and the outlet 111b is opened so that the region between the conduits 112 is open. One pressure P ₁ is introduced into the pressure transmission chamber 117 through the pressure transmission pipe 119, and the other pressure P ₂ is introduced into the pressure transmission chamber 118 through the pressure transmission pipe 120. do. Reference numerals 115 and 116 designate O rings.

In the above-described self-supporting regulating valve (II), when the differential pressure DELTA P between one pressure P ₁ and the other pressure P ₂ is equal to or larger than a set value, the spool 113 is shown by a dashed-dotted line in FIG. 2. It becomes the state shown. That is, the spool 113 comes into contact with the stopper 121, and the self-supporting regulating valve II is in a completely closed state. On the other hand, when the differential pressure DELTA P is less than the set value, the spool 113 is in a state shown by solid lines in FIG. That is, the spool 113 comes into contact with the stopper 122, and the self-supporting regulating valve II is in a fully open state.

Third Embodiment

3 is a structural diagram showing a self-supporting regulating valve according to a third embodiment of the present invention. Flowing through the self-standing control valve (Ⅲ), the conduit (12) the pressure (P ₁₎ of one of which is guided in a pressure transfer chamber (17) of the self-standing control valve (Ⅰ) shown in Figure 1 according to an embodiment of the invention; This is useful when applied to where it can be obtained from a fluid. In this case, it is because the pressure of the fluid to be controlled is applied to one end surface of the spool, so that the pressure of the fluid can be set to one pressure P ₁ . Due to the above features, the configuration of the self-supporting regulating valve III becomes simpler.

As shown in FIG. 3, the self-supporting regulating valve III according to the embodiment of the present invention, like the self-supporting regulating valve I shown in FIG. 1, has a valve body 31, a spool 33, and a preload spring. 34, a pressure transfer chamber 38, and a pressure transfer tube 40. Among the members, the valve body 31 is formed integrally with the conduit 32 via the inlet 31a of the fluid formed at one end of the valve body 31. The outlet part 31b for outflow of a fluid is formed in the center part of the valve main body 31, and the other pipeline 32 is connected to the outlet port 31b. The spool 33 is accommodated in the internal space of the valve body 31. The spool 33 has an L-shaped through hole 33a which communicates with the inlet port 31a and the outlet port 31b and is used as a fluid passage, and the spool 33 is provided in the inner space of the valve body 31. It can slide along the axial direction to the left-right direction of drawing. A predetermined preload is applied to the other end surface of the spool 33 by the preload spring 34. The O rings 35 and 36 are fitted on the outer circumferential surface at the left and right ends of the spool 33 to form a space between each end surface of the spool 33 and the other end surface inside the valve body 31. This space is used as the pressure transmission chamber 38, which receives the other pressure P ₂ through the pressure introduction hole 31d formed in the pressure transmission pipe 40 and the valve body 31. As shown in FIG.

In Figure 3, the one-way pressure (P ₁₎ and the other of the pressure (P ₂₎ than the pressure difference (△ P) between the set point was then shown that the self-standing control valve (Ⅲ) open. At this point, the left end surface of the spool 33 is in contact with the stopper 42 to limit the position of the spool. Conversely, when the differential pressure DELTA P decreases, the spool 33 moves to the right in the figure in accordance with the reduced amount. When the right end surface of the spool is in contact with the stopper 41, the spool 33 stops after the position of the spool is limited and becomes completely closed. As described above, when the spool 33 is in contact with the stopper 41, the self-supporting regulating valve III is in a completely closed state. When the spool 33 is in contact with the stopper 42, the self-supporting regulating valve III is fully open.

The above-mentioned self-supporting regulating valves (I, II, III) are variously used, and one of the preferred uses is to be used as a turbo-freezer. Therefore, the turbo-cooler equipped with the above-described self-supporting regulating valves (I, II, III) will be described in the fourth to eighth embodiments of the present invention.

Fourth Embodiment

4 is a system diagram showing a turbo-cooler according to a fourth embodiment of the present invention. The turbo-chiller is provided with a self-supporting regulating valve (I) instead of the intermediate intake valve 9 of the turbo-chiller shown in FIG. 9. Therefore, the same parts as in FIG. 9 are designated by the same reference numerals, and redundant description is omitted. In the figure, one of the pressures P ₁ of the self-supporting regulating valve I is the internal pressure of the condenser 6 guided through the pressure transmitting pipe 19 to the pressure transmitting chamber 17 (see FIG. 1), and the self-standing adjusting is performed. The other pressure P ₂ of the valve I is the internal pressure of the evaporator 1 which is guided through the pressure transmission pipe 20 to the pressure transmission chamber (see FIG. 1). Therefore, when P ₁ -P ₂ > P _ref1 (first setpoint), the self-standing valve I is opened and the refrigerant gas is discharged from the intermediate cooler 5 through the pipeline 10 of the turbo-compressor 4. Supply to the second stage. On the other hand, when P ₁ -P ₂ <P _ref1 , the self-supporting regulating valve I is closed and the supply of the refrigerant gas from the intermediate cooler 5 to the turbo-compressor is blocked. In the turbo-cooler, as described above, the differential pressure DELTA P between one pressure P _{1 that} is the internal pressure of the condenser 6 and the other pressure P _{2 that} is the internal pressure of the evaporator 1 is the first. Under conditions exceeding the set value P _ref1 , two-stage compression is performed by supplying the refrigerant gas from the intermediate cooler 5 to the turbo-compressor 4.

Fifth Embodiment

5 is a diagram according to a fifth embodiment of the present invention. For example, the turbo-compressor 4 of the turbo-cooler shown in FIG. 4 is extracted and expanded. In the figure, the turbo-compressor 4 is a refrigerant gas supplied from the evaporator 1 by the drive motor 51 rotating the impellers 53a and 53b (in the case of the two-stage compressor) via the speed increasing gear 52. It is configured to inhale and compress. The lubricating oil stored in the oil tank 54 is pumped up by the oil pump 55 and accumulated in the head tank 57a in the casing 57. Thereafter, the lubricating oil is supplied from the head tank 57a to a lubrication portion such as a speed increasing gear in an appropriate amount. The lubricating oil lubricating the speed increasing gear 52 and the like is returned to the oil tank 54. The casing 56 which accommodates the drive motor 51 and the casing 57 which accommodates the speed increasing gear 52 and the impellers 53a and 53b are separated from each other by the partition wall 58 so as to separate the motor chamber 59 and the gear. The chamber 60 is formed. This is to prevent the lubricating oil supplied to the speed increasing gear 52 from flowing into the motor chamber 59. For this purpose, the sealing portion (58) between the partition wall 58 and the rotary shaft 51a of the drive motor 51 facing the motor chamber 59 and the gear chamber 60 by puncturing the partition wall 58. 61) is provided. The seal 61 is generally formed from a gas seal or a floating seal, and the pressure of the motor chamber 59 is slightly higher than the pressure of the gear chamber 60 such that the gear chamber 60 in the motor chamber 59 is closed. To create a flow.

On the other hand, the motor chamber 59 of this type of turbo-compressor 4 is at atmospheric pressure of refrigerant gas, so that the refrigerant gas is between the casing 56 and the stator 51b of the drive motor 51 and between the stator 51b and the stator 51b. It flows between the rotor 51c, and cools the stator 51b and the rotor 51c. For this purpose, the right and left sides of the casing 56 are provided with a coolant supply port 56a and a coolant discharge port 56b, and a stator 56b and a rotor 51c are stacked between the casings. The high pressure refrigerant gas flows through the conduit 62 and the coolant supply port 56a to cool the stator 51b and the rotor 51c, and then through the coolant outlet 56b, for example, the evaporator 1 (Fig. 4).

As described above, in the turbo-compressor of this type, when the pressure in the motor chamber 59 is one pressure P ₁ and the pressure in the gear chamber 60 is the other pressure P ₂ , P _1. -P ₂ > P _ref2 (second setpoint) relationship must be established. Thus, in the prior art, the conduit 63 is provided with a flow rate limiting means such as an orifice. However, in this case, if a constant amount is set, the flow rate is fixed at this constant amount. Thus, a multi-perspective turbo-freezer, in which it is required to handle various loads due to non-uniform load setpoints, poses a problem in particular that orifices or the like do not succeed.

Therefore, according to the embodiment of the present invention, the self-supporting regulating valve I is placed in the conduit 63, and the internal pressure of the motor chamber 59, which is one pressure P ₁ of the self-standing regulating valve I, is pressurized. The internal pressure of the gear chamber 60, which is supplied to the pressure transmission chamber 17 (see FIG. 1) through the delivery pipe 19, and the pressure P _{2 on} the other side of the self-standing valve I, is transferred to the pressure transmission pipe ( 20 to a pressure transfer chamber 18 (see FIG. 1).

Therefore, according to the embodiment of the present invention, if P ₁ -P ₂ > P _ref2 (second set value), the self-standing valve I is opened so that the refrigerant gas for cooling is evaporator 1 (see FIG. 4) and the like. Is discharged. On the other hand, when P ₁ -P ₂ ≤ P _ref2 , the self-supporting regulating valve I is closed to increase the internal pressure of the motor chamber 59, whereby lubricating oil leaks from the gear chamber 60 to the motor chamber 59. To prevent them.

Sixth Embodiment

6 is a view according to a sixth embodiment of the present invention. For example, the turbo-compressor 4 of the turbo-cooler shown in FIG. 4 is extracted and expanded. The turbo-compressor 4 is of the same type as the turbo-compressor 4 shown in FIG. 5. Therefore, the same parts as in FIG. 5 are designated by the same reference numerals, and redundant description is omitted.

As shown in Fig. 6, the cooling refrigerant gas is supplied to the motor chamber 59 through the refrigerant supply port 56a. As shown by the arrows in the figure, the refrigerant gas flows between the casing 56 and the stator 51b and between the stator 51b and the rotor 51c to move the stator 51b and the rotor 51c. Cool. Thereafter, the refrigerant gas is discharged to the evaporator 1 (see FIG. 4), for example, through the refrigerant discharge port 56b. The flow rate of the refrigerant gas flowing between the casing 56 and the stator 51b and between the stator 51b and the rotor 51c includes the motor chamber 59 portion and the refrigerant outlet port (side) of the refrigerant supply port 56a. 56b) is determined by the pressure difference between the parts of the motor chamber 59 on the side. When the pressure difference is very large, the flow rate of the refrigerant gas increases to cause an increase in loss of the drive motor 51. If the pressure difference is very small, the flow rate of the refrigerant gas is reduced to obtain a sufficient cooling effect. Therefore, in the prior art, a pressure equalizing passage 71 is provided which communicates between the motor chamber 59 portion on the refrigerant supply port 56a side and the motor chamber 59 side on the refrigerant discharge port 56b, which equalizes the pressure equalizing tube 71. ) Is placed on the solenoid valve. When the pressure of the different portions is sensed and the sensed pressure difference exceeds the set value, the solenoid valve or the like is opened to bypass the refrigerant gas through the pressure equalizing line 71. However, the problems in the prior art require a pressure sensor and an expensive solenoid valve, the structure is complicated, and the cost is increased.

Therefore, according to the embodiment of the present invention, the self-supporting regulating valve I is placed in the conduit 63, and the internal pressure of the motor chamber 59, which is one pressure P ₁ of the self-standing regulating valve I, is pressurized. The internal pressure of the gear chamber 60, which is supplied to the pressure transmission chamber 17 (see FIG. 1) through the delivery pipe 19, and the pressure P _{2 on} the other side of the self-supporting regulating valve I, 20 to a pressure transfer chamber 18 (see FIG. 1).

Therefore, in the embodiment according to the present invention, if P ₁ -P ₂ > P _ref 3 (third set value), the self-standing valve I is opened and the refrigerant supply port 56a side through the pressure equalizing line 71. The refrigerant gas in the motor chamber 59 is bypassed. As a result, the flow rate of the refrigerant gas for cooling the stator 51b and the rotor 51c is limited, thereby limiting the load increase of the drive motor 51. On the other hand, P ₁ - P ₂ is ≤P _ref3, self-standing control valve (Ⅰ) is closed, all of the refrigerant gas supplied via a refrigerant supply port (56a) is used to cool the stator (51b) and a rotor (51c) Ensures satisfactory cooling of the corresponding part.

Seventh Embodiment

7 is a diagram according to a seventh embodiment of the present invention. For example, the turbo-compressor 4 of the turbo-cooler shown in FIG. 4 is extracted and expanded. The turbo-compressor 4 is of the same type as the turbo-compressor 4 shown in FIG. 5. Therefore, the same parts as in FIG. 5 are designated by the same reference numerals, and redundant description is omitted.

As shown in FIG. 7, the self-supporting regulating valve II is disposed in the middle of the pipeline 63a distributed from the condenser 6 to the casing 57, and the pressure P ₁ of one of the self-standing regulating valve II is provided. The internal pressure of the phosphor casing 57 acts through the pressure transmission pipe 19. As the other pressure P ₂ of the self-supporting regulating valve II, the oil pressure of the lubricating oil which is discharge oil pressure of the oil pump 55 acts. Therefore, when the pressure difference ΔP between the two pressures P ₁ and P ₂ falls short of the set value, the self-supporting regulating valve II is in an open state. Here, in the normal operation of the turbo-freezer, since the hydraulic pressure of the lubricating oil of the other pressure P ₂ is sufficiently higher than the pressure in the casing 57 which is the one pressure P ₁ , the self-supporting regulating valve II is It is closed.

On the other hand, when the oil pump 55 stops due to a power failure or the like, the supply of lubricating oil by the oil pump 55 is stopped. As a result, the oil pressure of the oil pump 55, that is, the pressure P ₂ , drops rapidly. Therefore, the differential pressure with the pressure P ₁ in the casing 57 exceeds the set value, and the self-standing valve II is opened. That is, when P ₁ -P ₂ > P _ref4 (fourth set value), the self-standing valve II is opened and the refrigerant is supplied from the condenser 6 via the conduit 63a. As a result, the liquid refrigerant in the condenser expanded by the stop of the turbo-cooler due to the power failure flows into the head tank 57a of the casing 57 and acts on the lubricating oil stored in the head tank 57a. The pressure of the refrigerant introduced into the head tank 57a replaces the function of the oil pump 55, thereby continuously supplying lubricating oil. Therefore, even if the supply of the lubricating oil is stopped, the lubricating oil can be continuously supplied to the rotating part which maintains rotation by the inertia force.

Eighth Embodiment

A turbo-compressor according to the prior art comprising a turbo-compressor according to the embodiment shown in Figs. 5 to 7 allows the rotation of the drive motor 51 (Figs. 5 to 7) to increase the speed gear 52 (Fig. 5). 7 to 7), it is generally applied to a system for delivery to the impellers 53a and 53b (FIGS. 5 to 7). In recent years, power supply of high frequency by an inverter becomes possible. Inverter control enables high speed operation of the drive motor (especially induction motor) 51. Therefore, a predetermined high speed operation of the drive motor 51 is possible without using the speed increasing gear 52, and the turbo-compressor which rotates the impellers 53a and 53b directly by the drive motor 51 (hereinafter, this type) Turbo-compressor is referred to as a direct drive turbo-compressor).

Since the direct type turbo-compressor does not have a speed increasing gear 52, lubrication of the portion is unnecessary, and it is sufficient that lubrication is performed only on the liquid bearing portion of the drive motor 51. Therefore, the refrigerant liquid having a lower viscosity and load bearing capability than the lubricant can be sufficiently used as the lubricant for the turbo-compressor.

In this state, a turbo-cooler using a refrigerant liquid as a lubricating liquid for a turbo-compressor has been proposed. The use of the self-supporting regulating valve (I) shown in FIG. 1 in a turbo-cooler of this type is shown in FIG. 8 as an eighth embodiment of the invention. The figure is a schematic diagram showing the main part of the turbo-chiller in extraction form. The same parts as in FIGS. 4 to 7 are denoted by the same reference numerals, and redundant descriptions are omitted.

As shown in FIG. 8, according to the turbo-cooler of the embodiment of the present invention, the hot, high-pressure refrigerant gas supplied from the turbo-compressor 4 via the check valve 74 is condensed by the condenser 6. To form a refrigerant liquid. The refrigerant liquid is supplied to the evaporator 1 through the expansion valve 72, and the refrigerant liquid is evaporated by the evaporator 1. The coolant flow path is shown by thick lines in the drawing as the main refrigerant system (IV). The bearing 73 rotatably supports the rotor 51c of the drive motor and is formed by a liquid bearing. For this purpose, the bearing 73 needs a lubricating oil supply. In the embodiment of the present invention, the lubrication system V is formed to use the refrigerant liquid as the lubricating liquid. That is, in the lubrication system V, the refrigerant liquid stored in the refrigerant tank 81 is driven by the refrigerant pump 82, flowed into the bearing 73 through the check valve 83, and then returned to the refrigerant tank 81. It is configured to come. The lubrication system (V) forms a closed loop separately from the main refrigerant system (IV).

In the lubrication system (V), when oil flows into the bearing 73, the refrigerant liquid necessarily contains a leakage amount, and it is necessary to compensate for this leakage amount. The amount corresponding to the leakage amount of the refrigerant liquid associated with the lubrication of the bearing 73 is returned to the evaporator 1 having the lowest pressure in the turbo-chiller. That the leakage amount returns to the evaporator 1 means that the refrigerant liquid of the lubrication system V must return to the main refrigerant system IV so that the corresponding amount of the refrigerant liquid must be replenished. Therefore, in the embodiment of the present invention, the liquid reservoir 84 of the condenser 6 and the inside of the coolant tank 81 communicate with each other by the conduit 85, and at the central portion passing through the conduit 85, The supplementary valve 86 is installed. That is, when the refrigerant replenishment valve 86 is opened, the refrigerant liquid stored in the liquid reservoir 84 flows into the refrigerant tank 81 by the pressure acting on it and is replenished. Opening and closing control of the refrigerant supplement valve 86 is performed by the level controller 87 which controls the liquid level of the refrigerant liquid in the refrigerant tank 81.

When the refrigerant replenishment valve 86 is opened to replenish the refrigerant tank 81 with the refrigerant liquid, the refrigerant gas in the expanded form of the refrigerant liquid flows into the refrigerant tank 81 with the refrigerant liquid. In other words, the refrigerant gas must be generated so as to increase the gas pressure inside the refrigerant tank 81, so that the refrigerant gas needs to be removed. Therefore, in a preferred embodiment of the present invention, the inside of the refrigerant tank 81 and the inside of the evaporator 1 communicate with each other by a conduit 88, and a communication valve 89 at the central portion passing through the conduit 88. Is installed.

When the refrigerant liquid to be replenished is introduced into the refrigerant tank 81, the refrigerant replenishment valve 86 is opened, and the delay is slightly delayed so that the communication valve 89 is opened, whereby the refrigerant liquid can be replenished, and the associated refrigerant gas Can be discharged to the evaporator 1 via the communication valve 89. That is, the inside of the refrigerant tank 81 can be replenished with refrigerant liquid while performing gas separation.

Since the refrigerant liquid introduced into the bearing 73 is heated, it is partially vaporized. When the final gas is left to stand, the refrigerant gas in the refrigerant tank 81 increases to increase the internal pressure. In order to avoid the above situation, in the embodiment of the present invention, the refrigerant gas inside the refrigerant tank 81 is condensed. Specifically, a heat transfer tube 90 is provided inside the refrigerant tank 81, and the refrigerant liquid is supplied from the condenser 6 to the heat transfer tube 90 through a restrictor 91, thereby providing a refrigerant tank 81. ) Is cooled to remove heat input in the bearing (73). As a result, the coolant liquid can be circulated, and the pressure inside the coolant tank 81 is kept constant. The refrigerant liquid left in the heating tube 90 is supplied to the evaporator 1.

The self-supporting regulating valve (I) communicating between the lubrication system (V) and the liquid reservoir (84) of the condenser (6) is installed in the middle of the conduit (94), and when the refrigerant pump (82) stops due to power failure or the like. Open state. That is, the refrigerant pump 82 stops at the time of power failure, and the refrigerant liquid circulation becomes impossible by the refrigerant pump 82. In contrast, the rotary part of the turbo-compressor 4 maintains rotation for a while by the inertia force even after the refrigerant pump 82 stops. Therefore, the lubrication of the bearing 73 during the inertia rotation of the rotating part must continue continuously. According to the embodiment of the present invention, one pressure P ₁ which is the internal pressure of the liquid reservoir 84 and the other pressure P _{2 which} is the pressure on the discharge side of the refrigerant pump 82 in the lubrication system V are described. ) Is supplied to the self-supporting regulating valve (I). As a result, when the refrigerant pump 82 operates normally and the refrigerant liquid circulates normally in the lubrication system V, if P ₁ -P ₂ ? P _ref5 , the self-supporting regulating valve I is in a closed state. When the refrigerant pump 82 stops due to a power failure or the like, the other pressure P ₂ decreases rapidly. As a result, if P ₁ -P ₂ > P _{ref 5} , the self-supporting regulating valve I is opened. Thus, the refrigerant liquid in the refrigerant reservoir 84 is supplied to the lubrication system V through the conduit 94. In this manner, even if the refrigerant pump 82 is stopped due to power failure or the like, the refrigerant liquid can be continuously introduced into the bearing for a while. In this case, the supply of the coolant liquid is carried out by the differential pressure between the condenser 6 and the lubrication system (V).

Furthermore, in the embodiment of the present invention, the rotor 5c and the like of the drive motor are cooled by the refrigerant gas. More specifically, a conduit 95 is provided to supply refrigerant from the liquid reservoir 84 of the condenser 6 to the casing of the drive motor, and a shrinkage valve 96 is provided in the middle of the conduit 95. Thus, the refrigerant liquid flowing out of the liquid reservoir 84 is adiabaticly expanded in the shrinkage valve 96 to be converted into a mist-containing saturated gas and supplied to the outer circumferential surface of the rotor 51c to supply the rotor 51c. Cool down. The refrigerant gas is liquefied while cooling the rotor 51c, forms a refrigerant liquid, and is discharged to the evaporator 1.

In the above-described turbo-freezer according to the embodiment of the present invention, the lubrication system V is provided separately from the main refrigeration system IV. Therefore, the lubrication system V is affected by the load variation of the main refrigeration system IV, but the refrigerant liquid is circulated by the drive of the refrigerant pump 82 to introduce the refrigerant liquid into the bearing 73. In this case, the refrigerant liquid heated in the bearing 73 is cooled by the refrigerant gas flowing through the heat transfer tube 90 to remove the input heat. As a result, the refrigerant liquid is always maintained at a constant pressure higher by a predetermined pressure α than the pressure inside the evaporator 1. At this constant pressure, the refrigerant liquid flows continuously into the bearing 73.

The level controller 85 detects the liquid level of the refrigerant liquid stored in the refrigerant tank 81, and when this liquid level is lowered to a predetermined value or less, the refrigerant refill valve 86 is opened to supply the replenishment refrigerant liquid.

When the refrigeration pump 82 stops due to a power failure or other cause during turbo-chiller operation, the other pressure P ₂ suddenly decreases, P ₁ -P ₂ > P _{ref 5} , and the self-standing valve I opens. . As a result, the lubrication system V communicates with the liquid reservoir 84 of the condenser 6 via a conduit 94. As a result, in accordance with the differential pressure between the condenser 6 and the lubrication system V, the lubrication system V continuously supplies the refrigerant liquid in the lubrication system V for a while. Therefore, the supply of the coolant liquid to the bearing 73 is continued to prevent sticking of the bearing 73.

The turbo-freezers according to the fourth to eighth embodiments described above use self-supporting regulating valves I or II in each part. However, any turbo-freezer can be used in combination with two or three freestanding regulating valves (I or II). That is, it may be a single turbo-freezer comprising a combination of turbo-freezers according to the fourth to eighth embodiments, or a single turbo-freezer comprising a combination of any two turbo-freezers.

Moreover, the turbo-cooler according to the fifth, sixth and eighth embodiments uses the self-supporting regulating valve I shown in FIG. 1, but of course the self-supporting regulating valve III shown in FIG. 3. You can also use That is, even if the independence adjustment valve I is replaced with the independence adjustment valve III, exactly the same operation and effect can be obtained in the above embodiment.

In the fourth to eighth embodiments, the turbo-chiller has been described without limitation. Compressive freezers, such as screw freezers, which compress the refrigerant may be constructed in the same way.

As mentioned above, the self-standing regulating valve according to the present invention, and a compression freezer comprising the self-standing regulating valve, are particularly useful when used in a compression freezer such as a turbo-freezer and a screw-type freezer.

Claims (8)

One pressure introduced into one pressure transmission chamber, which is a space formed between the cylindrical valve body and one end surface of the spool formed to be axially movable in the internal space of the valve body, acts on one end surface of the spool, The other pressure introduced into the other pressure transmission chamber, which is a space formed between the valve body and the other end surface of the spool, and the spring force of the preload spring act on the other end surface of the spool, The through hole is installed in the spool, When the pressure difference between one pressure and the other pressure exceeds the set value, the through hole and the pipe connected to the valve body communicate with each other, and the self-standing valve is opened while the through hole and the pipe are not opened when the pressure difference does not exceed the set value. Independent control valve is characterized in that the shut-off self-regulation valve is configured to be closed. One pressure flowing into one pressure transmission chamber, which is a space formed between the cylindrical valve body and the flange portion provided in the middle of the spool, acts on the flange portion of the spool, The other pressure flowing into the other pressure transmission chamber, which is a space formed between the valve body and one end surface of the spool movably formed in the inner space of the valve body, acts on one end surface of the spool, The spool is moved in accordance with the pressure difference between one pressure and the other pressure, so that the other end surface of the spool closes or opens the region between the open ends of the two conduits connected to the valve body. On one end surface of the spool formed axially movable in the inner space of the cylindrical valve body, the pressure of the fluid controlled by the self-supporting regulating valve acts as one pressure, The other pressure flowing into the pressure transmission chamber, which is a space formed between the valve body and the other end surface of the spool, and the spring force of the preload spring act on the other end surface of the spool, A through hole communicating with one end of the spool and a conduit connected to the valve body is provided. When the pressure difference between one pressure and the other pressure exceeds the set value, the through hole and the pipe connected to the valve body communicate with each other, and the self-standing valve is opened while the through hole and the pipe are not opened when the pressure difference does not exceed the set value. Independent control valve is characterized in that the shut-off self-regulation valve is configured to be closed. In a multi-stage compressed refrigerator with an intermediate cooler, The self-supporting regulating valve of claim 1 is interposed in the middle of the pipeline that returns the refrigerant from the intermediate cooler to the compressor. The internal pressure of the condenser acts as one pressure to the self-standing valve, The internal pressure of the evaporator acts as the other pressure to the self-supporting regulating valve, And the self-standing valve is open when the pressure difference between the two pressures exceeds a set value. Separating the casing for accommodating the drive motor of the compressor from the casing for accommodating the speed increase gear and the impeller, A sealing means is provided in the gap between the partition wall and the rotating shaft penetrating the partition wall so that the lubricating oil lubricating the speed increase gear does not flow into the casing of the drive motor side. After cooling the respective parts of the drive motor by introducing a refrigerant gas into the drive motor side casing, 12. A compressed refrigerator having a compressor configured to discharge the refrigerant gas from a casing, The self-supporting regulating valve of claim 1 is interposed in the middle of the pipeline for discharging the cooling refrigerant from the drive motor side casing. The internal pressure of the drive motor side casing acts as a pressure to the self-standing valve, The internal pressure of the speed increasing gear side casing acts as the other pressure on the self-supporting regulating valve, And when the pressure difference between the two pressures exceeds the set value, the self-supporting regulating valve is opened. After cooling the respective parts of the drive motor by flowing refrigerant gas into the drive motor side casing of the compressor, 12. A compressed refrigerator having a compressor configured to discharge the refrigerant gas from a casing, The self-standing valve according to claim 1 or 3 is interposed in the casing of the drive motor in the middle of a pressure equalizing pipe for equalizing the pressure at the coolant supply port side into which the cooling coolant flows and the pressure at the coolant discharge port at which the coolant discharges. The internal pressure on the refrigerant supply port side of the casing acts as a pressure on the self-standing valve, The internal pressure on the refrigerant outlet side of the casing acts as the other pressure on the self-standing valve. And when the pressure difference between the two pressures exceeds the set value, the self-supporting regulating valve is opened. Store lubricant in the casing, In a compression type refrigerator having a compressor configured to circulate this lubricant with an oil pump to lubricate the rotating part, In the middle of the pipeline from the condenser to the casing, the self-standing valve according to claim 2 is interposed, The internal pressure of the casing acts as one pressure to the self-standing valve, The hydraulic pressure of the lubricating oil acts as the other pressure to the self-supporting regulating valve, And the self-standing valve is open when the pressure difference between the two pressures is less than the set value. A rotary compressor is configured to be rotatably supported by a fluid bearing using a refrigerant liquid as a working fluid, and after condensing the high-temperature and high-pressure refrigerant gas formed by the compression of the compressor by a condenser, it is supplied to an evaporator. A main refrigerant system configured to evaporate to return to the compressor as refrigerant gas, A main refrigerant system and a lubrication system comprising a refrigerant tank for storing refrigerant liquid and a refrigerant pump, and independently installed a lubrication system configured to circulate the refrigerant liquid pumped by the refrigerant pump into the bearing part of the compressor. A compressed refrigerator comprising a system, The self-standing valve of claim 1 is interposed in the middle of the pipeline communicating between the liquid reservoir of the condenser and the pipeline forming the lubrication system, The internal pressure of the liquid reservoir acts as one pressure on the self-standing valve, The internal pressure of the duct of the lubrication system acts as the other pressure to the self-standing valve And when the pressure difference between the two pressures exceeds the set value, the self-supporting regulating valve is opened.