JP2005282938A - Cooling device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve energy-saving performance and controllability by preventing the generation of water-hammer phenomenon (shock and vibration) due to cooling water when cooling a condenser with a water cooled type cooling unit, and improving operating efficiency over the whole. <P>SOLUTION: The condenser 4 provided in a refrigeration cycle 2 is provided with the water cooled type cooling unit 5 for cooling the condenser 4 by exchanging heat by circulating cooling water Ws. The water cooled type cooling unit 5 is provided with a water control means 6 for controlling flow of the cooling water Ws on the basis of the refrigerant pressure Pd in a high-pressure range of the refrigeration cycle 2 and a pressure absorbing means 7 for absorbing the refrigerant pressure Pd and for transmitting it to the water control means 6. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a cooling device that cools an object to be cooled by circulating a coolant to the object to be cooled.

  In general, in a laser processing machine, it is necessary to ensure thermal stability for optical components such as mirrors, which greatly affect the processing accuracy, and to avoid deterioration in processing quality. High cooling accuracy and cooling performance that can sufficiently follow relatively large load fluctuations due to workpiece material, plate thickness, machining speed, and machined surface roughness, etc. are required. Japanese Patent Laid-Open No. 9-134220 proposed a cooling device (temperature control method for a cooling device) that meets such requirements. In this cooling device, a liquid feed pump is connected to a supply port of a coolant tank that stores a coolant, and a coolant inlet of an object to be cooled such as a laser processing machine is connected to a discharge port of the liquid feed pump. A cooler is connected to the return port of the coolant tank, and the coolant outlet of the object to be cooled is connected to the inlet of the cooler.

  However, since this cooling device stores the cooled cooling liquid in the cooling liquid tank, there is an advantage that a cooling liquid with a stable temperature can always be supplied to the object to be cooled. Are limited, there is a problem to be solved such as a reduction in COP (coefficient of performance = cooling capacity / input power) of the refrigerant circuit, a relatively large pressure resistance required on the object to be cooled, The present applicant has already proposed a cooling device that has solved this problem in Japanese Patent Laid-Open No. 2003-329355.

The cooling device includes a cooling liquid tank that stores the cooling liquid returned from the object to be cooled, a liquid feeding pump that sends out the cooling liquid flowing out from the supply port of the cooling liquid tank, and a cooling liquid that is discharged from the liquid feeding pump. A cooler that cools the liquid by heat exchange and supplies it to the object to be cooled is provided. The temperature of the coolant flowing out of the cooler is detected by a temperature sensor, and the cooling temperature of the cooler is controlled based on the detected temperature. A control system, more specifically, a control system having an inverter control of the rotation frequency of the compressor in the refrigeration cycle for circulating the refrigerant in the cooler based on the temperature detected by the temperature sensor is provided.
JP-A-9-134220 JP 2003-329355 A

  However, the conventional cooling device using the refrigeration cycle in which the rotation frequency of the compressor is inverter-controlled has the following problems to be solved.

  First, when a water-cooled cooling unit is attached to the condenser provided for the refrigeration cycle, a water control valve that controls the flow rate of the cooling water is usually connected, and the refrigerant pressure on the discharge side of the condenser is adjusted to that of the water control valve. The opening of the water control valve can be varied by applying it to the control port.In other words, the opening of the water control valve is increased when the refrigerant pressure becomes high, and the opening of the water control valve when the refrigerant pressure is low. However, when the refrigerant pressure fluctuates sharply, a large water hammer phenomenon (impact or vibration) that cannot be ignored by the cooling water occurs in the water control valve.

  Second, the inverter control of the compressor varies the rotation frequency of the compressor by a control signal given to the inverter circuit from the control unit, so there is a limit to the range of the rotation frequency that can be controlled, and usually 30 [ %] In the low load region below, inverter control becomes difficult. For this reason, in the low load region, the actual situation is that the hot gas bypass circuit is controlled by opening and closing, which causes a decrease in the overall operation efficiency, and there are difficulties in energy saving and controllability.

  The object of the present invention is to provide a cooling device that solves the problems in the background art.

  In order to solve the above-described problem, the present invention cools the coolant W by the cooler 3 connected to the refrigeration cycle 2 and circulates the cooled coolant W through the coolant M to cool the coolant M. When the cooling device 1 for performing the above is configured, the condenser 4 provided in the refrigeration cycle 2 is provided with a water cooling type cooling unit 5 for cooling the condenser 4 by heat exchange by circulating the cooling water Ws. A water control means 6 for controlling the flow rate of the cooling water Ws based on the refrigerant pressure Pd in the high pressure region in the refrigeration cycle 2, and a pressure buffer means 7 for buffering the refrigerant pressure Pd and transmitting it to the water control means 6. Is provided.

  In this case, according to a preferred aspect of the invention, the water control means 6 includes a water control valve 6v that controls the flow rate of the cooling water Ws according to the magnitude of the control pressure Px applied to the control port 6vc, and the pressure buffering means. 7, a capillary tube 7 c that applies the refrigerant pressure Pd to the control port 6 vc can be used. The refrigeration cycle 2 is provided with a digital control refrigerant 13 provided with a digital switching mechanism 13 for switching to a loaded state in which refrigerant compression is performed during operation of the compressor motor 12 or an unloaded state in which refrigerant compression is released during operation of the compressor motor 12. A compressor 11 can be used. Further, the cooling device 1 is provided with a coolant tank 15 that stores the coolant W and a liquid feed pump 16 that supplies the coolant W stored in the coolant tank 15 to the object M to be cooled. The cooler 3 that cools the coolant W returned to the coolant tank 15 or the coolant W supplied from the coolant tank 15 to the object M to be cooled can be provided.

  According to the cooling device 1 according to the present invention having such a configuration, the following remarkable effects can be obtained.

  (1) Even when the condenser 4 provided in the refrigeration cycle 2 is cooled by the water cooling type cooling unit 5, the refrigerant pressure Pd is buffered by the pressure buffering means 7 and transmitted to the water control means 6, so that the refrigerant pressure Pd Even if there is a steep fluctuation, it is possible to prevent the water hammer phenomenon (impact or vibration) from occurring due to the cooling water Ws in the water control means 6.

  (2) According to a preferred embodiment, the water control means 6 uses a water control valve 6v that controls the flow rate of the cooling water Ws according to the magnitude of the control pressure Px applied to the control port 6vc, and the pressure buffer means 7 If the capillary tube 7c that applies the refrigerant pressure Pd to the control port 6vc is used, a simple configuration is sufficient, which can contribute to ease of implementation and low cost.

  (3) According to a preferred embodiment, the refrigeration cycle 2 is provided with a digital switching mechanism unit 13 for switching to a load state in which refrigerant compression is performed when the compressor motor 12 is operated or an unload state in which refrigerant compression is released when the compressor motor 12 is operated. When the provided digitally controlled refrigerant compressor 11 is used, a large water hammer phenomenon is likely to occur due to steep fluctuations in the refrigerant pressure Pd due to repeated loading and unloading conditions, but this water hammer phenomenon can be avoided reliably and effectively. can do.

  (4) According to a preferred embodiment, the refrigeration cycle 2 is provided with a digital switching mechanism unit 13 for switching to a load state in which refrigerant compression is performed when the compressor motor 12 is operated or an unload state in which refrigerant compression is released when the compressor motor 12 is operated. If the provided digitally controlled refrigerant compressor 11 is used, the control range can be greatly expanded. In particular, control is possible even in a low load region of 30% or less with respect to the maximum cooling capacity, which was the limit in the conventional inverter control, and since no inverter circuit is required, the overall operating efficiency is reduced. Thus, energy saving and controllability can be improved.

  Next, the best embodiment according to the present invention will be given and described in detail with reference to the drawings.

  First, the configuration of the cooling device 1 according to the present embodiment will be specifically described with reference to FIGS.

  In FIG. 2, 1 indicates the overall configuration of the cooling device according to the present embodiment, and M indicates an object to be cooled such as a laser processing machine connected to the cooling device 1. The cooling device 1 is connected to the object to be cooled M, and the object to be cooled M can be cooled by circulating the coolant W through the object to be cooled M. The cooling device 1 includes a coolant tank 15 that stores the coolant W, a liquid feed pump 16 that supplies the coolant W stored in the coolant tank 15 to the object M to be cooled, and a coolant tank from the object M to be cooled. A cooler 3 such as a plate heat exchanger that cools the coolant W returned to 15, and a refrigeration cycle 2 that is connected to the cooler 3 and cools the coolant W passing through the cooler 3 by heat exchange; And a control system 20 that controls the entire cooling device 1.

  In this case, the cooling liquid tank 15 stores the cooling liquid W such as cooling water, and includes a liquid supply port, a drain port, a liquid level gauge, a ball tap, and the like that are not shown. Further, as shown in FIG. 2, a hydraulic pressure gauge 21, a liquid temperature sensor 22, a bypass valve 23, pipe joints 24a and 24b, etc. connected to the water supply path are provided between the coolant tank 15 and the object M to be cooled. .

  On the other hand, as shown in FIG. 2, the refrigeration cycle 2 includes a condenser 4, a refrigerant dryer 26, an electronic expansion valve 27, an accumulator 28, and a digital control refrigerant compressor 11 as main functional units. The refrigerant inflow side of the electronic expansion valve 27 is connected to the refrigerant inflow side, and the refrigerant inflow side of the accumulator 28 is connected to the refrigerant outflow side of the cooler 3. Thereby, a refrigerant circuit in which the refrigerant K circulates in the direction of the arrow Fk is configured. The basic function of the refrigeration cycle 2 is the same as a known refrigeration cycle.

  Further, the condenser 4 is provided with a water cooling type cooling unit 5. As shown in FIGS. 1 and 2, the water-cooled cooling unit 5 supplies the cooling water Ws to the heat exchange unit 71 that performs heat exchange with the condenser 4, the water supply port 71i of the heat exchange unit 71, and The cooling water supply part 72 which receives the cooling water Ws discharged | emitted from the drain port 71o of the heat exchange part 71 is provided, and the function which cools the said condenser 4 by heat exchange by circulating the cooling water Ws with respect to the condenser 4 Have Further, the water-cooled cooling unit 5 has a water control means for controlling the flow rate of the cooling water Ws based on the refrigerant pressure Pd in the high pressure region (between the discharge port of the refrigerant compressor 11 and the expansion valve 27) in the refrigeration cycle 2. 6 and a pressure buffering means 7 for buffering the refrigerant pressure Pd and transmitting it to the water control means 6. In this case, the water control means 6 is connected to the cooling water supply part 72 and the water supply pipe 73i connected to the water supply port 71i, and depending on the control pressure Px applied to the control port 6vc, the water supply pipe 73i. In addition, a water control valve 6v that controls the flow rate of the cooling water Ws flowing therethrough is used, and a capillary tube 7c that applies a refrigerant pressure Pd to the control port 6vc is used as the pressure buffer means 7. Reference numeral 74 denotes a freeze prevention valve that is manually operated and connected in parallel to the water control valve 6v, and 75 denotes an ambient temperature sensor that detects the ambient temperature Tr.

  In addition, in the refrigeration cycle 2 shown in FIG. 2, 31 is a low pressure switch, 32 is a low pressure gauge, 33 is a suction temperature sensor, 34 is a high pressure switch, 35 is a clogging alarm pressure switch, 36 is a high pressure gauge, Reference numeral 37 denotes a condenser outlet temperature sensor, and 38 denotes an evaporator inlet temperature sensor. Each of these pressure switches 31... Mainly functions as a protection switch.

  On the other hand, as shown in FIGS. 3 to 5, the digitally controlled refrigerant compressor 11 includes a refrigerant compression unit 14 having an orbiting scroll 18 and a fixed scroll 19, and is loaded by displacing the fixed scroll 19 in the axial direction Fc. A digital switching mechanism 13 for switching to a state (see FIG. 3) or an unloaded state (see FIG. 4) is provided. As the digitally controlled refrigerant compressor 11 having such a function, a “scroll machine having a capacity adjusting mechanism” disclosed in JP-A-8-334094 can be used.

  Next, the structure of the digital control refrigerant compressor 11 provided with such a digital switching mechanism part 13 is demonstrated with reference to FIGS. Reference numeral 45 denotes a compressor body. The compressor main body 45 includes a sealed casing 46, and a compressor motor 12 having a rotary shaft 12s protruding upward is built in a lower portion of the casing 46. A refrigerant compressor 14 and a digital switching mechanism 13 are disposed above the compressor motor 12. In this case, the upper space of the compressor motor 12 is divided into upper and lower spaces by a partition wall 48, and has a discharge chamber Co on the upper side of the partition wall 48 and a suction chamber Ci on the lower side. The casing 46 has a refrigerant discharge port 49 facing the discharge chamber Co and a refrigerant suction port 50 facing the suction chamber Ci on the peripheral surface of the casing 46.

  Further, a fixed support plate 51 is disposed inside the suction chamber Ci, and the orbiting scroll 18 is placed on the upper surface of the support plate 51, and the fixed scroll 19 is placed on the orbiting scroll 18 to compress the refrigerant. Part 14 is configured. In this case, the orbiting scroll 18 has the spiral blade 18f on the upper surface and the engaged portion 52 at the center of the lower surface. The engaged portion 53 is engaged with an engaging portion 53 at the upper end eccentric position of the rotating shaft 12s. Thereby, if the rotating shaft 12s rotates, the orbiting scroll 18 turns on the orbit. On the other hand, the fixed scroll 19 is supported so as to be displaceable in the axial direction Fc by a plurality of guide posts 54 provided on the support plate 51, and the position in the direction perpendicular to the axial direction Fc is fixed. The fixed scroll 19 has a spiral wing 19f on the lower surface and a protruding portion 55 at the center of the upper surface. The projecting portion 55 reaches the discharge chamber Co through an insertion hole 48 s provided at the center of the partition wall 48. Inside the projecting portion 55, there is an air passage 55 r for communicating the central space Pc existing below the fixed scroll 19 and the discharge chamber Co, and a ram portion 56 is integrally formed at the upper end of the projecting portion 55. The ram portion 56 is accommodated in a cylinder portion 57 attached to the upper surface of the casing 46. Thus, a cylinder chamber 57r is provided between the cylinder portion 57 and the ram portion 56. The ram portion 56 has a bleed hole 56s that allows the cylinder chamber 57r and the discharge chamber Co to communicate with each other.

  On the other hand, the cylinder chamber 57r and the refrigerant suction port 50 are connected by a communication pipe 58, and an electromagnetic valve 59 for opening and closing the communication pipe 58 is connected in the middle of the communication pipe 58, and between the electromagnetic valve 59 and the cylinder chamber 57r. A spare valve 60 that opens and closes the communication pipe 58 is connected to the communication pipe 58. In this case, the electromagnetic valve 59 constitutes a part of the digital switching mechanism unit 13. Reference numeral 61 denotes a discharge temperature sensor that detects the temperature of the refrigerant K discharged from the digital control refrigerant compressor 11. The refrigerant suction port 50 in the compressor main body 45 is connected to the refrigerant outflow side of the accumulator 28 via the series-connected check valve 40, and the refrigerant discharge port 49 in the compressor main body 45 is connected in series to the check valve. It connects to the refrigerant inflow side of the condenser 4 via the valve 41.

  In addition, the control system 20 includes a control unit 65. The controller 65 mainly has a function of controlling the actuators of each unit based on detection results obtained from sensors such as temperature and pressure. Therefore, the liquid temperature sensor 22, the suction temperature sensor 33, the discharge temperature sensor 61, the ambient temperature sensor 75, the condenser outlet temperature sensor 37, the evaporator inlet temperature sensor 38, and the like are connected to the input port of the control unit 65, respectively. In addition, the compressor motor 12, the electromagnetic valve 59, the spare valve 60, the cooling water supply unit 72, the electromagnetic expansion valve 27, and the like of the compressor main body 45 are connected to the output port of the control unit 65, respectively. Furthermore, the control unit 65 has a computer function and a communication function that can execute various processes and controls.

  Next, operation | movement (usage method) of the cooling device 1 which concerns on this embodiment is demonstrated with reference to FIGS.

  First, the operation (principle) of the digitally controlled refrigerant compressor 11 used in the cooling device 1 will be described with reference to FIGS. As described above, the digitally-controlled refrigerant compressor 11 includes the refrigerant compressor 14 having the orbiting scroll 18 and the fixed scroll 19 and displaces the fixed scroll 19 in the axial direction Fc, thereby operating the compressor motor 12. There is provided a digital switching mechanism 13 for switching to a load state (FIG. 3) where refrigerant compression is sometimes performed or an unload state (FIG. 4) where refrigerant compression is released when the compressor motor 12 is operated.

  In the digitally controlled refrigerant compressor 11, the rotation shaft 12s is rotated by operating the compressor motor 12, and the engaging portion 53 at the upper end eccentric position of the rotation shaft 12s rotates around the rotation shaft 12s. To do. As a result, the engaged portion 52 that engages and follows the engaging portion 53 and the orbital scroll 18 also orbit on the orbit. On the other hand, since the fixed scroll 19 is fixed (regulated) at a position perpendicular to the axial direction Fc, the spiral wing 18f of the orbiting scroll 18 and the spiral wing 19f of the fixed scroll 19 are shown in FIG. Relative motion as shown in (b) is performed.

  On the other hand, the refrigerant K is supplied from the refrigerant suction port 50 to the suction chamber Ci. Now, as shown in FIG. 3, it is assumed that the plunger 59p of the electromagnetic valve 59 protrudes, that is, the communication pipe 58 is in a closed state. The spare valve 60 is set in an open state. In this state, since the internal pressure of the cylinder chamber 57r is higher than the internal pressure of the suction chamber Ci on the low pressure side, the urging force by a spring (not shown) that pushes up the ram portion 56 is overcome, and the spiral blade 19f of the fixed scroll 19 Then, it is pressed against the orbiting scroll 18. FIG. 3 shows this state.

  Therefore, if the relative position of the spiral wing 18f of the orbiting scroll 18 with respect to the spiral wing 19f of the fixed scroll 19 is in the state shown in FIG. 5A, the refrigerant K present in the suction chamber Ci follows the direction of the dotted arrow. It enters between the spiral wings 18f and 19f from the outside. When the orbiting scroll 18 orbits on the orbit and the relative position of the spiral blade 18f with respect to the spiral blade 19f is in the state shown in FIG. 5B, the refrigerant K that has entered between the spiral blades 18f and 19f is It is enclosed in a crescent-shaped sealed space Pm ... formed between 18f and 19f. As the orbiting scroll 18 turns, the volume of the crescent-shaped sealed space Pm... Gradually decreases, the refrigerant K is compressed, and when the refrigerant K reaches the central space Pc, the pressure of the refrigerant K is increased. Become the maximum. Thereafter, the compressed refrigerant K in the central space Pc reaches the discharge chamber Co through the air passage 55 r and is discharged from the refrigerant discharge port 49. The distribution path of the refrigerant K at this time is indicated by a dotted arrow in FIG. Therefore, this state becomes a load state in which the refrigerant is compressed by the digital control refrigerant compressor 11, and the output is 100%.

  On the other hand, it is assumed that the electromagnetic valve 59 is controlled and the communication pipe 58 is switched to the open state by retracting the plunger 59p as shown in FIG. In this state, the suction chamber Ci on the low pressure side and the cylinder chamber 57r communicate with each other through the communication pipe 58, and the internal pressure of the cylinder chamber 57r and the internal pressure of the suction chamber Ci become the same pressure. 56 is displaced upward. As a result, as shown in FIG. 4, the spiral wing 19 f of the fixed scroll 19 is separated from the orbiting scroll 18, and a gap G is generated between the orbiting scroll 18 and the fixed scroll 19. As a result, the refrigerant K is not compressed. The distribution path of the refrigerant K at this time is indicated by a dotted arrow in FIG. Therefore, this state is an unloaded state in which the refrigerant compression by the digitally controlled refrigerant compressor 11 is released, and the output is 0 [%].

  FIG. 6 shows a valve control signal Sp applied to the electromagnetic valve 59. In FIG. 6, tr represents a control section in the load state (100 [%] output state), and tn represents a control section in the unload state (0 [%] output state), and the cooling according to the present embodiment. Control of the digitally controlled refrigerant compressor 11 used in the apparatus 1 is performed by changing the load rate Rr (= Tr / (Tr + Tn)). As described above, the control for the digital control refrigerant compressor 11 used in the cooling device 1 according to the present embodiment is digital control in which the time axis of the load state “1” and the unload state “0” is varied, and the conventional inverter control That is, the control form is fundamentally different from the analog control that varies the rotation frequency (size) of the compressor.

  Next, the overall operation (usage method) of the cooling device 1 will be described. First, as shown in FIG. 2, the cooling device 1 is connected to an object to be cooled M via pipe joints 24 a and 24 b, and a cooling liquid (cooling water or the like) W is accommodated in the cooling liquid tank 15. . Accordingly, when the liquid feeding pump 16 is operated, the cooling liquid W in the cooling liquid tank 15 is sent out from the supply port 15s by the liquid feeding pump 16 and supplied to the object to be cooled M through the pipe joint 24a. Then, the object to be cooled M is cooled. On the other hand, the coolant W warmed by cooling (heat exchange) of the object to be cooled M is supplied to the cooler 3 through the pipe joint 24b. In the cooler 3, heat exchange is performed between the supplied coolant W and the coolant K cooled in the refrigeration cycle 2, and the coolant W is cooled by the coolant K. Then, the coolant W cooled by the cooler 3 is returned to the return port 15 r of the coolant tank 15 and stored in the coolant tank 15. In FIG. 2, the arrow Fw indicates the flow direction of the coolant W.

  On the other hand, the temperature (liquid temperature Tw) of the coolant W supplied to the object to be cooled M is detected by the liquid temperature sensor 22, and this detection signal is given to the controller 65. The control unit 65 controls the digital control refrigerant compressor 11 based on the detection signal, that is, performs digital control for opening and closing the electromagnetic valve 59 described above, and performs feedback control so that the liquid temperature Tw becomes the target temperature.

  Therefore, according to such a cooling device 1, the temperature control for the coolant W uses digital control that controls the time axis so that the digitally controlled refrigerant compressor 11 is in a loaded state or an unloaded state. The range can be expanded dramatically. In particular, control is possible even in a low load region of 30% or less with respect to the maximum cooling capacity, which was the limit in the conventional inverter control, and since no inverter circuit is required, the overall operating efficiency is reduced. Will improve dramatically. As a result, energy saving and controllability were improved, and improvement of about 65 [%] at maximum was achieved with respect to conventional inverter control.

  By the way, in the cooling device 1 according to the present embodiment, the digitally controlled refrigerant compressor 11 is selected on the time axis so as to be in a load state (100 [%] output state) or an unload state (0 [%] output state). The temperature of the coolant W flowing out of the cooler 3 has a large amplitude and fluctuates with a frequent cycle (control frequency) as shown in the temperature change characteristic Qs shown by the phantom line in FIG. Resulting in. Therefore, in such a cooling device 1, when a configuration in which the cooler 3 is connected in front of the object to be cooled M as in JP-A-2003-329355, the coolant W cooled by the cooler 3 is used. Is supplied to the cooled object M as it is, and the cooling characteristic (behavior) of the cooler 3 directly affects the temperature of the coolant W. In particular, when the frequency of digital control is high (the cycle is short), the liquid temperature is also averaged due to responsiveness, but the cycle is set to be relatively long in consideration of energy saving and controllability. In such a case, the influence on the coolant W is increased. However, in the cooling device 1 according to the present embodiment, the configuration in which the coolant W is temporarily stored in the coolant tank 15 is combined with the cooler 3 to which the refrigeration cycle 2 including the digitally controlled refrigerant compressor 11 is connected. While the temperature of the coolant W can be surely averaged, the above-described effect, that is, the overall operation efficiency is dramatically improved, and the basic effect that energy saving and controllability is improved is ensured. As shown by the temperature change characteristic Ps indicated by a solid line in FIG. 7, it is possible to obtain the cooling liquid W with high cooling accuracy and stable liquid temperature Tw.

  In addition, the digital switching mechanism unit 13 includes the refrigerant compression unit 14 using the orbiting scroll 18 and the fixed scroll 19, and displaces the fixed scroll 19 or the orbiting scroll 18 in the axial direction Fc to switch to the loaded state or the unloaded state. Since the digitally controlled refrigerant compressor 11 is used, the target cooling device 1 can be realized easily and at low cost by a relatively simple configuration (principle).

  The above description is the basic operation of the cooling device 1 according to the present embodiment, but the cooling device 1 further includes the following unique configuration and functions, and performs unique control.

  First, rapid fluctuations in refrigerant pressure are reduced by check valves 40 and 41 connected in series on the upstream side and downstream side of the digitally controlled refrigerant compressor 11. The digitally controlled refrigerant compressor 11 is switched to a load state (100 [%] output state) or an unload state (0 [%] output state) by the digital switching mechanism unit 13, whereby temperature control for the coolant W is performed. Done. In this case, when switching from the load state to the unload state or from the unload state to the load state, the refrigerant pressure fluctuates abruptly, and this fluctuation frequently occurs. Therefore, the pressure gauges 32 and 36 in the refrigerant circuit, etc. Inconveniences such as shortening of the service life of the parts used, and deterioration of detection accuracy of the temperature sensors 61, 37, etc. occur. Therefore, in order to eliminate this problem, check valves 40 and 41 are connected in series on the upstream side and the downstream side of the digitally controlled refrigerant compressor 11, respectively, to reduce rapid fluctuations in the refrigerant pressure. As a result, the refrigerant pressure and the refrigerant temperature can be stabilized, and the service life of the parts used in the refrigerant circuit can be extended, and further, the detection accuracy can be improved and stabilized.

  Further, the load rate Rr is monitored, and as shown in FIG. 8, when the load rate Rr is lower than the set value Xc (illustrated 28 [%]), two control modes can be selected. Since the cooling device 1 uses the digitally controlled refrigerant compressor 11, unlike the conventional inverter control, the cooling device 1 is switched to a low load state of 28% or less, and further to an unload state even in a no-load state. This makes it possible to control the temperature. In this case, high accuracy and controllability with respect to temperature control can be obtained even in the low load region, but the power consumption increases because the compressor motor 12 is in an operating state. Therefore, when the accuracy and controllability of temperature control are more important than ensuring energy saving in the low load region, the first control mode in which the switching control between the unload state and the load state is continuously performed can be selected. In addition, in the case where energy saving is more important than the accuracy and controllability of temperature control in the low load region, the second control mode for ON / OFF control of the compressor motor 12 can be selected. The load [%] in FIG. 8 is the ratio of the maximum cooling capacity of the cooling device 1 to the amount of heat exchanged in the cooler 3.

  On the other hand, the operation of the condenser 4 which is a main part of the present embodiment is as follows. First, the condenser 4 is connected to the subsequent stage of the digital control refrigerant compressor 11 and functions as a heat exchanger for cooling and condensing the high-temperature and high-pressure refrigerant K compressed by the digital control refrigerant compressor 11. It is cooled by the water cooling type cooling unit 5 provided. In this case, the cooling water Ws discharged from the cooling water supply unit 72 is supplied to the water supply port 71i of the heat exchange unit 71 via the water control valve 6v, and reaches the drain port 71o through the inside of the heat exchange unit 71. The water is returned from the drain port 71o to the cooling water supply unit 72. The returned cooling water Ws is cooled again by the cooling water supply unit 72 and supplied to the water supply port 71i, and the cooling water Ws is circulated, and the heat exchange unit 71 passes through the condenser 4 at a high temperature. Heat exchange is performed between the high-pressure refrigerant K and the cooling water Ws. The freeze prevention valve 74 is in a closed state. Further, in FIG. 1, an arrow Fx indicates the circulation direction of the cooling water Ws.

  Furthermore, the pressure of the refrigerant K discharged from the condenser 4 (refrigerant pressure Pd) is applied to the control port 6vc of the water control valve 6v through a capillary tube 7c formed by a thin tube. At this time, the refrigerant pressure Pd is buffered by the capillary tube 7c, and the buffered control pressure Px is applied to the control port 6vc. Thereby, when the refrigerant pressure Pd becomes high, the opening degree of the water control valve 6v is increased to increase the flow rate (water supply amount), and when the refrigerant pressure Pd becomes low, the water control valve 6v is opened. The flow rate (water supply amount) is reduced by reducing the degree, and the internal pressure of the condenser 4 is stabilized (stabilized).

  By the way, in the cooling device 1 according to the present embodiment, the digital control refrigerant compressor 11 is used. As described above, the digital control refrigerant compressor 11 is loaded by the digital switching mechanism 13 so that the refrigerant is compressed when the compressor motor 12 is operated, or is unloaded when the compressor motor 12 is released. Since the operation of switching to is repeated, the pressure of the refrigerant K discharged from the digitally controlled refrigerant compressor 11 (discharged refrigerant pressure) repeats large and steep fluctuations. Therefore, when the refrigerant pressure Pd is directly applied to the control port 6vc of the water control valve 6v without being buffered by the pressure buffer means 7 (capillary tube 7c), a large water hammer that cannot be ignored due to the cooling water Ws in the water control valve 6v. Phenomenon (shock or vibration) occurs.

  However, in the cooling device 1 according to this embodiment, the refrigerant pressure Pd is buffered, that is, converted into the gently changing control pressure Px by the capillary tube 7c, and this control pressure Px is transferred to the control port 6vc of the water control valve 6v. Therefore, the water hammer phenomenon (impact or vibration) due to the cooling water Ws is reliably and effectively avoided. Basically, a simple configuration by adding (exchange) the capillary tube 7c is sufficient, which can contribute to ease of implementation and low cost. The control unit 65 can control the cooling temperature for the cooling water Ws in the cooling water supply unit 72, and at this time, the ambient temperature Tr detected by the ambient temperature sensor 75 (the outside air temperature around the condenser 4). Based on the above, the cooling temperature for the cooling water Ws can be controlled.

  On the other hand, the spare valve 60 is connected as a countermeasure against failure of the electromagnetic valve 59. Since the electromagnetic valve 59 is used for digital control, the ON / OFF operation is repeated at a considerable frequency and is a part whose durability is questioned. However, when the electromagnetic valve 59 breaks down, the refrigerant compressor 6 It becomes virtually inoperable. Therefore, the spare valve 60 is provided as a countermeasure. Now, when the electromagnetic valve 59 fails in the open state, the liquid temperature Tw detected by the liquid temperature sensor 22 rises and exceeds the upper limit value, so that it is detected as an abnormality. Therefore, the control unit 65 controls the spare valve 60 to the closed side and switches to the ON / OFF control of the compressor motor 4. On the other hand, when the electromagnetic valve 59 fails in the closed state, the liquid temperature Tw detected by the liquid temperature sensor 22 falls and exceeds the lower limit value, so that it is detected as abnormal. Therefore, the control unit 65 switches to ON / OFF control of the compressor motor 4. In this case, the failure is notified by turning on an alarm lamp or the like, but in any case, the operation can be continued temporarily.

  In addition, in FIG. 8, the cooling device 1 which concerns on the modified embodiment of this invention is shown. The cooling device 1 according to this modified embodiment is obtained by changing the connection part of the cooler 3 with respect to the cooling device 1 shown in FIG. That is, in the cooling device 1 according to the modified embodiment, the cooling liquid W supplied from the cooling liquid tank 15 to the object to be cooled M is cooled by the cooler 3. Therefore, in the cooling device 1 according to the modified embodiment, the cooling liquid W can be cooled quickly or the like, if the setting such as increasing the control frequency of digital control is performed on the cooling device 1 shown in FIG. The cooling control of the coolant W can be quickly stopped, and an accurate control response can be obtained when the object to be cooled M requires sophisticated and complicated cooling characteristics or when a sudden temperature fluctuation occurs due to some cause. Sex can be secured. As a result, accurate and flexible control can be performed, and advanced cooling characteristics corresponding to the object to be cooled M can be easily realized. In addition, in FIG. 8, the code | symbol 2m has shown the refrigeration cycle main body except the cooler 3 from the refrigeration cycle 2 shown in FIG. In addition, in FIG. 8, the same parts as those in FIG. 2 are denoted by the same reference numerals to clarify the configuration, and detailed description thereof is omitted.

  Although the best embodiment has been described in detail above, the present invention is not limited to such an embodiment, and departs from the gist of the present invention in the detailed configuration, shape, material, quantity, numerical value, and the like. It can be changed, added, or deleted as long as it is not. For example, the digitally-controlled refrigerant compressor 11 may be a refrigerant compressor in which the digital switching mechanism unit 13 is provided in a refrigerant compressor other than the example. Moreover, although the water control valve 6v (and the freeze prevention valve 74) illustrated the case where it connected to the water supply port 71i side of the heat exchange part 71, you may connect it to the drain port 71o side of the heat exchange part 71. Furthermore, while the water control valve 6v is used as the water control means 6 and the capillary tube 7c is used as the pressure buffer means 7, the water control valve 6v and the capillary tube 7c have the same functions. On the other hand, when the refrigerant pressure Pd is transmitted by electrical means or mechanical means, a necessary buffering process is performed for the magnitude of the electrical signal or the mechanical displacement amount. You can also. On the other hand, the present invention is optimally applied to the refrigeration cycle 2 including the digitally controlled refrigerant compressor 11 provided with the digital switching mechanism unit 13, but can be similarly applied to the case of using other forms of refrigerant compressors (compressors). . In addition, the compressor motor 12 in the present invention is a concept including all devices that are rotated by various kinds of power such as an internal combustion engine (engine) as well as an electric motor.

The circuit block diagram which extracts and shows the digital control refrigerant compressor and condenser of the refrigerating cycle in the cooling device concerning the best embodiment of the present invention, Circuit configuration diagram of the cooling device, Cross-sectional configuration diagram of a load state showing a part of a digitally controlled refrigerant compressor provided for the refrigeration cycle of the cooling device Cross-sectional configuration diagram of an unloaded state showing a part of the digitally controlled refrigerant compressor, Action explanatory diagram showing the relationship between the start scroll and the fixed scroll in the digital control refrigerant compressor, Signal waveform diagram of valve control signal to be given to the digitally controlled refrigerant compressor, Liquid temperature change characteristic diagram with respect to time when using the cooling device, The circuit block diagram which abbreviate | omitted a part of cooling device which concerns on the modified embodiment of this invention,

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cooling device 2 Refrigerating cycle 3 Cooler 4 Condenser 5 Water cooling type cooling part 6 Water control means 6v Water control valve 6vc Control port 7 Pressure buffer means 7c Capillary tube 11 Digital control refrigerant compressor 12 Compressor motor 13 Digital switching mechanism part 15 Coolant tank 16 Liquid feed pump W Coolant M Object to be cooled Pd Refrigerant pressure Ws Coolant water Px Control pressure

Claims (4)

  In the cooling device that cools the cooling object by cooling the cooling liquid with a cooler connected to the refrigeration cycle and circulating the cooled cooling liquid to the cooling object, cooling water is supplied to the condenser provided in the refrigeration cycle. And a water-cooled cooling unit that cools the condenser by heat exchange, and controls the flow rate of the cooling water based on the refrigerant pressure in the high-pressure region in the refrigeration cycle. A cooling device comprising water means and pressure buffering means for buffering the refrigerant pressure and transmitting it to the water control means.   The water control means uses a water control valve that controls the flow rate of the cooling water according to the magnitude of the control pressure applied to the control port, and the capillary tube that applies the refrigerant pressure to the control port to the pressure buffer means The cooling device according to claim 1, wherein:   The refrigeration cycle includes a digitally controlled refrigerant compressor provided with a digital switching mechanism that switches to a loaded state in which refrigerant compression is performed during operation of the compressor motor or an unloaded state in which refrigerant compression is released during operation of the compressor motor. The cooling device according to claim 1.   A cooling liquid tank that stores the cooling liquid and a liquid feed pump that supplies the cooling liquid stored in the cooling liquid tank to the object to be cooled, and the cooling liquid returned from the cooling object to the cooling liquid tank or the cooling The cooling device according to claim 1, further comprising a cooler that cools the coolant supplied from the liquid tank to the object to be cooled.

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