KR101108311B1 - Heating system and automatic vending machine - Google Patents

Abstract

The waste heat at the time of cooling is used for warming, and the power consumption for switching and maintaining the cooling and heating can be reduced to further reduce the power consumption, and the amount of refrigerant used for the hydrocarbon refrigerant can be kept to a minimum. It is possible to realize high-precision temperature adjustment of goods such as canned beverages by optimizing the adjustment of the capacity, and to provide a heating system and a vending machine that can maintain the temperature of the compressor at a high temperature to improve the heating capacity.

Description

Heating system and vending machine {HEATING SYSTEM AND AUTOMATIC VENDING MACHINE}

1 is a refrigerant circuit diagram of a vending machine according to Embodiment 1 of the present invention;

2 is a view showing a working pressure range of the compressor of the vending machine of the embodiment;

3 is a diagram showing the capability of the compressor of the vending machine of the embodiment;

4 is a diagram showing the efficiency of the compressor of the vending machine of the embodiment;

5 is a sectional view of the compressor of the vending machine of the embodiment;

6 is a refrigerant circuit diagram of a cooling heating system according to an embodiment of the present invention;

FIG. 7 is a diagram showing characteristics of the amount of refrigerant dissolved in oil of mineral oil A according to the embodiment of the present invention; FIG.

8 is a diagram showing the characteristic of the oil viscosity of the mineral oil (A) according to the embodiment of the present invention;

9 is a view showing the characteristics of the amount of refrigerant dissolved in oil of mineral oil (B) according to the embodiment of the present invention;

10 is a view showing the characteristic of viscosity of mineral oil (B) according to the embodiment of the present invention;                 

11 is a refrigerant circuit diagram of a vending machine according to an embodiment of the present invention;

12 is a timing chart of heating control of a vending machine according to an embodiment of the present invention;

13 is a refrigerant circuit diagram of a vending machine according to an embodiment of the present invention;

14 is a timing chart of a heating control of the vending machine according to the embodiment of the present invention;

15 is a refrigeration cycle diagram of the vending machine according to the embodiment of the present invention;

16 is a longitudinal sectional view of the vending machine in the embodiment of the present invention;

17A is a plan view of a machine room of the vending machine according to the embodiment of the present invention;

17B is a sectional view of the machine room of the vending machine in the embodiment of the present invention;

18 is a refrigeration cycle diagram of the vending machine according to the embodiment of the present invention;

19 is an entire longitudinal sectional view of the vending machine according to the embodiment of the present invention;

20 is a sectional view of a machine room of the vending machine according to the embodiment of the present invention;

21 is a perspective view of an outdoor heat exchanger in the embodiment of the present invention;

Fig. 22 is a sectional view of the machine room of the vending machine in the embodiment of the present invention;

23 is a refrigerant circuit diagram of a conventional vending machine;

24 is a refrigerant circuit diagram of a conventional cooling heating system;

25 is a refrigerant circuit diagram of a conventional vending machine;

26 is a timing chart of a heating control of a conventional vending machine,

27 is a refrigerant circuit diagram of a conventional vending machine;                 

28 is a configuration diagram of a control device of a conventional vending machine;

29 is a configuration diagram of a conventional vending machine,

30A is a configuration diagram of a conventional compressor insulation member;

30B is a configuration diagram of a conventional compressor insulation member.

<Explanation of symbols for the main parts of the drawings>

101: hot / cold switching room 102: cold dedicated room

103: second cold exclusive chamber 120: high temperature receiver type compressor

121: switching room condenser 122: switching room evaporator

123: expansion valve for heating 211: sensor

212 heater 213 fan

220: low pressure shell compressor 221: cover

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a vending machine that uses a latent heat generated when a refrigerant compressed by a compressor is condensed in a vending machine for cooling or selling products such as canned drinks at the same time as heating.

In recent years, the demand for power consumption reduction for vending machines has increased, and as a means for reducing power consumption, it has been proposed to use waste heat generated by cooling. Such a proposal is disclosed, for example, in Japanese Patent Laid-Open No. 5-233941.                         

A conventional vending machine will be described below with reference to the drawings.

23 is a refrigerant circuit diagram of a conventional vending machine.

As shown in Fig. 23, a conventional vending machine includes a storage chamber including a hot / cold switching chamber 101, a cold dedicated chamber 102, and a second cold dedicated chamber 103, and includes a hot / cold switching chamber ( The indoor heat exchanger 104 installed in the 101, the evaporator 105 installed in the cold dedicated chamber 102, the second evaporator 106 installed in the second cold dedicated chamber 102, the outdoor heat exchanger 107 installed outside the storage compartment, the compressor It has a cooling heating system consisting of 108.

In addition, the expansion valve A109, the expansion valve B110, and the expansion valve C111 each have a function of closing and reducing the pressure of the refrigerant passing therethrough, and the opening / closing valve A112, the opening / closing valve B113, the opening / closing valve, respectively. C114 and the shut-off valve D115 control the presence or absence of the flow of the refrigerant, respectively.

The operation of the conventional vending machine configured as described above will be described below.

In the case of cooling the hot / cold switching room 101, the on / off valve A112 and the on / off valve D115 are opened, and the on / off valve B113 and the on / off valve C114 are closed. The compressor 108 is driven. After the refrigerant discharged from the compressor 108 is condensed in the outdoor heat exchanger 107, the refrigerant is depressurized by the expansion valve A109, the expansion valve B110, and the expansion valve C111, respectively, and the indoor heat exchanger 104, The evaporator 105 and the second evaporator 106 are supplied. The refrigerant evaporated in the indoor heat exchanger 104, the evaporator 105, and the second evaporator 106 is refluxed to the compressor 108.                         

At this time, the storage chamber that has reached a predetermined temperature in the hot / cold switching chamber 101, the cold dedicated chamber 102, and the second cold dedicated chamber 103 includes a corresponding expansion valve A109, expansion valve B110, and expansion. The valve C111 is closed to stop the supply of the refrigerant. In addition, when all the storage chambers reach the predetermined temperature, the operation of the compressor 108 is stopped.

Next, when the hot / cold switching room 101 is heated, the on / off valve A112, the on / off valve D115 and the expansion valve A109 are closed, and the on / off valve B13 and the on / off valve C114 are opened. Thus, the compressor 108 is driven. A part of the refrigerant discharged from the compressor 1108 is condensed in the indoor heat exchanger 104 and again condensed in the outdoor heat exchanger 107, and then decompressed in the expansion valve B110 and the expansion valve C111, respectively. The evaporator 105 and the second evaporator 106 are supplied. Then, the refrigerant evaporated in the evaporator 105 and the second evaporator 106 is refluxed to the compressor 108. In the cold exclusive chamber 102 and the second cold exclusive chamber 103, the storage chamber that has reached a predetermined temperature closes the corresponding expansion valve B110 and expansion valve C111 to stop the supply of the refrigerant. In addition, when all the storage chambers reach the predetermined temperature, the operation of the compressor 108 is stopped.

Here, the hot / cold switching chamber 101 can be efficiently heated by using the condensed waste heat of the refrigerant generated when cooling the cold exclusive chamber 102 and the second cold exclusive chamber 103, so that an additional heater such as an electric heater may be used. The amount of power consumption can be reduced as compared with the case where the hot / cold switching room 101 is heated using a heating means.

Moreover, the structure which maintains the temperature of the lubricating oil in a compressor more than a constant by heating a compressor with a heater conventionally, or the structure using the special lubricating oil which has a comparatively small melt | dissolution amount of a hydrocarbon refrigerant is proposed. These proposals are disclosed in Japanese Patent Laid-Open No. 2000-283621 and Japanese Patent Laid-Open No. 2001-234184. Here, a general mineral oil-based lubricating oil is used in a refrigerator using a hydrocarbon refrigerant. Since the low-pressure shell type compressor is used only at a low evaporation temperature, the amount of the refrigerant dissolved in the lubricating oil is not a big problem. The amount of refrigerant dissolved in the lubricant of the compressor is a problem in the case of a cooling system using a heat pump or a high pressure shell compressor having a relatively high evaporation temperature.

Hereinafter, the above-mentioned conventional cooling heating system is demonstrated, referring drawings.

24 is a refrigerant circuit diagram of a conventional cooling heating system.

As shown in Fig. 24, in the conventional cooling and heating system, propane or isobutane, which is a hydrocarbon refrigerant, is used, and the high pressure shell compressor 201, the four-way valve 202, the accumulator 203, and the outdoor heat exchanger 4 are used. The indoor heat exchanger 205 has a basic configuration. In this way, in the case of cooling the room, the refrigerant discharged from the high-pressure shell compressor 201 switches the flow path to the four-way valve 202, is supplied from the outdoor heat exchanger 204 to the indoor heat exchanger 205, and again the four-way valve ( Reflux from the accumulator 203 to the high pressure shell compressor 201 via 202. At the same time, when the room is warmed, the refrigerant discharged from the high pressure shell compressor 201 is switched to the four-way valve 202 and is supplied from the indoor heat exchanger 205 to the outdoor heat exchanger 204. In this way, it flows back from the accumulator 203 to the high pressure shell-type compressor 201 via the four-way valve 1202.

Here, generally, the indoor heat exchanger 205 is installed in a heat insulating space (not shown, hereinafter referred to as a storage chamber) in which the object to be cooled and heated, such as canned beverage, is stored, and at the same time, a high pressure shell compressor 201 and a four-way valve. 202, the accumulator 203, and the outdoor heat exchanger 204 are disposed outside the adiabatic space.

In addition, the piping connecting the outdoor heat exchanger 204 and the indoor heat exchanger 205 includes a heating capillary tube 206, a cooling check valve 207, a cooling capillary tube 208, and the like. The heating check valve 209 and the dryer 210 are connected. Here, the heating capillary tube 206, the cooling check valve 207, the cooling capillary tube 208, and the heating check valve 209 are connected in parallel, respectively, and the heating capillary tube 206 is connected. ) And a dryer 210 at a position fitted to the cooling capillary tube 208. In addition, in general, the outdoor heat exchanger 204 and the indoor heat exchanger 205 are each blown by an independent blower fan (not shown) as needed, and air cooling and heat exchange are promoted.

Here, the outlet pipe of the high pressure shell compressor 201 includes a sensor 211 for measuring the temperature of the discharge gas, and a heater 212 for heating the bottom surface of the shell under the high pressure shell compressor 201 and the high pressure shell compressor 201. ), The fan 213 for air cooling is provided.

The operation | movement is demonstrated below about the conventional cold / hot switching system comprised as mentioned above.

When the inside of the storage chamber is cooled, the refrigerant discharged from the high-pressure shell compressor 201 switches the flow path to the four-way valve 202 and is supplied to the outdoor heat exchanger 204 to liquefy condensation. The liquid refrigerant exited from the outdoor heat exchanger 204 is supplied to the dryer 210 via the cooling check valve 207. The liquid refrigerant exited from the dryer 210 is reduced in the cooling capillary tube 208, supplied to the indoor heat exchanger 205, and evaporated to evaporate, and the gas refrigerant passes through the four-way valve 202 to accumulate 203. From the high pressure shell compressor 201.

In addition, when the inside of the storage chamber is heated, the refrigerant discharged from the high pressure shell-type compressor 201 switches the flow path to the four-way valve 202 and is supplied to the indoor heat exchanger 205 to condense and liquefy. The liquid refrigerant exited from the indoor heat exchanger 205 is supplied to the dryer 210 via the heating check valve 209. Then, the liquid refrigerant exited from the dryer 210 is decompressed to the heating capillary tube 206, supplied to the outdoor heat exchanger 204, and evaporated to vaporize, and the gas refrigerant passes through the four-way valve 202 to accumulate 203. From the high pressure shell compressor 201.

Here, when the high pressure shell compressor 201 is used, the mineral oil-based lubricating oil stored in the high pressure shell compressor 201 is exposed to the hydrocarbon refrigerant at the condensation pressure to dissolve the hydrocarbon refrigerant. In general, it is known to dissolve a large amount of hydrocarbon refrigerant when the temperature of mineral oil-based lubricant is low. Therefore, the indication value of the sensor 211 is always monitored, and when it is lower than the predetermined value, it energizes the heater 212, and when it is higher than the predetermined value, the fan 213 is driven to air-cool, thereby providing high pressure shell compressor 201. ) And the temperature of the lubricating oil stored therein is kept substantially constant high.

Thus, by using the heater 212 and the fan 213 to maintain the temperature of the high-pressure shell compressor 201 approximately constant, the amount of refrigerant in the lubricating oil can be kept small and approximately constant, thereby preventing an increase in the amount of refrigerant used. can do.                         

In addition, in recent years, demand for power consumption reduction for vending machines is increasing, and as a means for reducing power consumption, it is proposed to heat products such as canned beverages by using a heat pump system using waste heat generated by cooling or atmospheric heat. It is.

In addition, since the heat pump system has poor starting characteristics, especially at low outside temperatures, the vending machine can increase the rotational speed of the compressor at low outside temperatures or start up, increase the heating capacity, and supplement the heating capacity using an auxiliary heater. Proposed. Such a proposal is disclosed, for example, in Japanese Patent Laid-Open No. 2002-288726.

A conventional vending machine will be described below with reference to the drawings.

25 is a refrigerant circuit diagram of a conventional vending machine, and FIG. 26 is a time chart showing heating control of the conventional vending machine.

As illustrated in FIG. 25, a conventional vending machine includes a storage chamber including a hot / cold switching chamber 301, a cold dedicated chamber 302, and a second cold dedicated chamber 303, and a hot / cold switching chamber 301. Indoor heat exchanger 304, the evaporator 305 installed in the cold dedicated chamber 302, the second evaporator 306 installed in the second cold dedicated chamber 302, the outdoor heat exchanger 307, compressor installed outside the storage compartment 308 has a heat pump system. Here, the compressor 308 controls the capability by changing the rotational speed corresponding to the change in the room temperature of each storage compartment.

In addition, the expansion valve (A309), expansion valve (B310), expansion valve (C311) has a function of closing and reducing the pressure of the refrigerant passing through, respectively, the on-off valve (A312), on-off valve (B313), opening and closing The valve C314 and the on / off valve D315 control the presence or absence of the flow of the refrigerant, respectively.

In addition, in order to complement the heating capacity of the heat pump system, an auxiliary heater 316 made of an electric heater having a heating capacity almost half of that of the heat pump system is installed above the wind of the indoor heat exchanger 304. have.

The operation of the conventional vending machine configured as described above will be described below.

When cooling the hot / cold switching room 301, the on-off valve A312 and the on-off valve D315 are opened, the on-off valve B313 and the on-off valve C314 are closed, and the compressor 308 is driven. . The refrigerant discharged from the compressor 308 is condensed in the outdoor heat exchanger 307, and then depressurized in the expansion valve A309, the expansion valve B310, and the expansion valve C311, respectively, and the indoor heat exchanger 304, The evaporator 305 and the second evaporator 306 are supplied. The refrigerant evaporated in the indoor heat exchanger 304, the evaporator 305, and the second evaporator 306 is refluxed to the compressor 308.

At this time, the storage chamber that has reached a predetermined temperature in the hot / cold switching chamber 301, the cold dedicated chamber 302, and the second cold dedicated chamber 303 has a corresponding expansion valve A309, expansion valve B310, and expansion. The valve C311 is closed to stop the supply of the refrigerant. In addition, when all the storage chambers reach the predetermined temperature, the operation of the compressor 308 is stopped.

Next, when the hot / cold switching room 301 is heated, the on-off valve A312, the on-off valve D315, and the expansion valve A309 are closed, and the on-off valve B313 and the on-off valve C314 are opened. Thus, the compressor 308 is driven. Part of the refrigerant discharged from the compressor 308 is condensed in the indoor heat exchanger 304 and condensed in the outdoor heat exchanger 307, and then decompressed in the expansion valve B310 and the expansion valve C311, respectively. The evaporator 305 and the second evaporator 306 are supplied. The refrigerant evaporated in the evaporator 305 and the second evaporator 306 is refluxed to the compressor 308. In the cold exclusive chamber 302 and the second cold exclusive chamber 303, the storage chamber that has reached a predetermined temperature closes the corresponding expansion valve B310 and expansion valve C311 to stop the supply of the refrigerant. In addition, the compressor 308 stops operation when all the storage chambers reach the predetermined temperature.

Here, the hot / cold switching chamber 301 can be efficiently heated by using the condensed waste heat of the refrigerant generated when the cold dedicated chamber 302 and the second cold dedicated chamber 303 are cooled, so that an additional heater such as an electric heater can be used. The amount of power consumption can be reduced as compared with the case where the hot / cold switching room 301 is heated using a heating means.

Next, the change of the rotation speed of the compressor 308 and the ON / OFF state of the auxiliary heater 316 with respect to the room temperature change of the hot / cold switching room 301 at the time of heating is demonstrated in detail using FIG. do.

FIG. 26 is a time chart in which time divisions t0 to t27 are defined on the horizontal axis, the change in the room temperature of the hot / cold switching room 301 in order from the top, the change in the condensation temperature of the indoor heat exchanger 304, and the auxiliary heater 316. The total sum of the heating capacity of the heat pump system which consists of the ON / OFF state of the motor, the rotation speed of the compressor 308, the auxiliary heater 316, the compressor 308, etc. is shown. In addition, T0 described on the vertical axis of the room temperature is the ambient temperature, T1 is the heater ON temperature as a reference for inserting the auxiliary heater 316, heater OFF temperature as a reference for cutting the auxiliary heater 316, and T2 is the compressor 308. The shift UP temperature, T3, which is a reference for increasing the rotational speed of, denotes the shift DOWN temperature, which is a reference for reducing the rotational speed of the compressor 308. In addition, Tp described on the vertical axis of the condensation temperature is a target temperature at the time of warming of the product stored in the hot / cold switching room 301, and Tq is a condensation temperature of the upper limit which is preferable for securing the reliability of the compressor 308. Indicates.

Here, the auxiliary heater 316 turns ON when the room temperature becomes lower than the heater ON temperature, and turns OFF when the auxiliary heater 316 becomes equal to or higher than the heater OFF temperature. In addition, the compressor 308 increases the rotational speed in the order of N1, N2, N3, N4 when the room temperature is lower than the shift UP temperature, and increases the rotational speed in the order of N4, N3, N2, N1 when the temperature is higher than the shift-down temperature. Slow down. In general, in the compressor 308 having a compression mechanism of the receiver type, the minimum rotational speed N1 is about 20 to 30 rpm, and the ratio of the minimum rotational speed N1 and the highest rotational speed N4 is set to about one to three to four. As described above, changing the rotational speed of the compressor 308 discontinuously in order to avoid abnormal vibration or noise caused by resonating at a specific rotational speed, is particularly useful in equipment installed indoors such as vending machines. It is important.

In FIG. 26, the time t0 is an initial starting state in which the room temperature has dropped to near the outside temperature T0, and since the room temperature is lower than T1, the auxiliary heater 316 is turned ON. In addition, the compressor 308 is operated at the highest rotation speed N4. This is because a large warming capacity is required in the initial starting state, and thus the compressor 308 is forcibly operated at the maximum rotational speed N4 by detecting the initial starting state from power supply or door opening and closing.                         

When the room temperature exceeds T1 at the time t3, the auxiliary heater 316 is turned off. When the room temperature exceeds T3 at the time t8, the compressor 308 decelerates to the minimum rotational speed N1. The decrease in the rotational speed of the compressor 308 from N4 to N1 at time t8 is for suppressing excessive temperature rise in room temperature occurring in the interval of time t8 to t13. Since the compressor 308 was operated at the highest rotation speed N4 for a long time in the initial starting state, the condensation temperature is increased so that the indoor heat exchanger 304 and the peripheral member become excessive temperature rise in the interval of time t6 to t8. Even if the rotational speed of 308 is gradually lowered, the heating capacity does not decrease. Therefore, the rotational speed of the compressor 308 is lowered at once.

Then, by maintaining the compressor 308 at the minimum rotational speed N1 in the interval of the times t8 to t18, the room temperature gradually decreases, and if the room temperature falls below T2 at the time t19, the compressor 308 is gradually increased from the rotational speed N1 to N4. Goes. As a result, the condensation temperature of the indoor heat exchanger 304 rises again, and the warming ability rises, and the room temperature rises again after the time t22.

After that, if the room temperature exceeds T3, the compressor 308 is gradually decelerated, and if the room temperature falls below T2, the compressor 308 is sequentially increased to sequentially stabilize the room temperature. In addition, even when the compressor 308 is operated at the minimum rotational speed N1 when the heated load is high due to high outside temperature, if the room temperature rises further than T3 and exceeds the upper limit temperature (not shown) of the room temperature, the operation of the compressor 308 is stopped. Stop.

In this way, by controlling the capacity of the compressor 308 at a temperature higher than the heater ON temperature and the heater OFF temperature of the auxiliary heater 316, an efficient heat pump is suppressed while suppressing heating by the auxiliary heater 316 extremely. It is possible to realize stable control at room temperature.

Moreover, it is preferable to set the waiting time until the next change is made after changing the time interval which the compressor 308 increases or decreases sequentially, ie, the rotation speed of the compressor 308, It is desirable to set it about several to several ten minutes. Even if the rotation speed of the compressor 308 is rapidly increased or decelerated, the heating capacity cannot be changed rapidly. Therefore, if the rotation speed of the compressor 308 is changed rapidly after the room temperature is stabilized, the excessive temperature rise of the indoor heat exchanger 304 is increased. Increases, rather increases room temperature fluctuations.

In addition, by installing the auxiliary heater 316 above the wind of the indoor heat exchanger 304, air higher than the room temperature can be supplied to the indoor heat exchanger 304 in the initial starting state where the room temperature is particularly low. It can be expected to shorten the time until the start of the condensation temperature rises.

Moreover, the conventional vending machine is proposed the system which heats up with a heat pump for the purpose of energy saving. Such a proposal is disclosed in Japanese Patent Laid-Open No. 2002-277147.

27 shows a refrigerant circuit diagram of a conventional vending machine described in Japanese Patent Laid-Open No. 2002-277147. As shown in FIG. 27, the vault inside the vending machine is divided into three, a cooling exclusive storage (hereinafter referred to as a left chamber), a cooling heating chamber B (hereinafter referred to as a solid chamber), and a cooling heating chamber C (hereinafter referred to as a lower compartment). The use side unit 401A (specific use side unit), the use side unit 401B, and the use side unit 401C which are mentioned later are respectively provided, and each unit is provided with the blower, respectively. . The heat source side unit 402 and the blower 420 are provided outside the vault of the vending machine. And the cooling-heating apparatus of a vending machine is comprised by these heat source side units 402 and utilization side units 401A-401C.

Next, the refrigerant circuit will be described. The heat source side unit 402 is composed of a compressor 418, a heat source side heat exchanger 419, a gas-liquid separator 421, and the like, and the use side units 401A, 401B and 401C are used side heat exchangers. 412A, 412B, and 412C. Then, the heat source side heat exchanger 419 is branch-connected to the refrigerant discharge pipe 403 and the refrigerant suction pipe 404 of the compressor 418 to the switching valves 405A and 405B. On the other hand, the high-pressure gas pipe 407 and the refrigerant suction pipe 404 which branch-connect the pipe 406 between the heat source side unit 402 and the utilization side unit 401A, 401B, and 401C to the refrigerant discharge pipe 403. ) And a low pressure gas pipe 408 and a liquid pipe 409 connected to each other.

The use side heat exchanger 412A of the use side unit 401A is connected to the low pressure gas pipe 408, and is connected to the liquid pipe 409 via a refrigerant flow rate control valve 414 such as an electric expansion valve. . In addition, the use side heat exchanger 412B, 412C of the use side unit 401B, 401C is branch-connected to the high pressure gas pipe 407 and the low pressure gas pipe 408 via switching valves 410A, 410B, 411A, and 411B, respectively. The liquid pipe 409 is connected to refrigerant flow control valves 415 and 416 such as an electric expansion valve.

In addition, a refrigerant flow rate control valve 417 such as an electric expansion valve is interposed in the liquid pipe 409. In addition, since the left chamber only cools, the switching valves 410A, 410B, 41LA, and 411B, which are the same as the usage-side units 401B and 401C, are not provided in the usage-side unit 401A. It may be possible to branch-connect with the 403 and the refrigerant suction pipe 404 to enable the temporary temperature. In addition, the left chamber may be a heating-only store, in which case the use-side heat exchanger 412A is naturally connected to the high-pressure gas pipe 407.

Here, when the capacity of each heat exchanger of the prior art sets the capacity of the use side heat exchanger 412B to 1, the capacity of the use side heat exchanger 412C is 2, the capacity of the use side heat exchanger 412A is 3, The capacity of the heat source side heat exchanger 419 is set to be six.

Next, FIG. 28 shows the block diagram of the control apparatus of the conventional vending machine described in Unexamined-Japanese-Patent No. 2002-277147. As shown in FIG. 28, the control apparatus C is comprised by the general-purpose microcomputer 422, The temperature as a temperature selection means attached to the selection button of a product and each of a left chamber, a solid chamber, and a right chamber on an input side is shown. Sensors 423A, 423B and 423C are connected. Further, on the output side of the microcomputer 422, each switching valve 405A, 405B, 410A, 410B, 411A, 411B, each refrigerant flow control valve 414, 415, 416, and a refrigerant flow control valve 417 And a compressor 418, each blower, and each product discharging device are connected.

29 shows a block diagram of a conventional vending machine described in Japanese Patent Laid-Open No. 2002-277147. As shown in FIG. 29, the compressor 418 and the heat source side heat exchanger 419 are provided in the same air path, and it is comprised so that the heat exchange fan 420 may heat-exchange simultaneously.

The operation of the vending machine configured as described above will be described below.

First, the case where the goods are cooled by using the whole of the left chamber, the solid chamber and the right chamber as a refrigerator is described.

When the temperature detected by the temperature sensors 423A, 423B, and 423C is equal to or higher than the cooling set temperature, the microcomputer 422 opens the switching valve 405A of the refrigerant discharge pipe 403 of the heat source side heat exchanger 419. The switching valve 405B of the refrigerant suction pipe 404 is closed, and the switching valves 410A and 411A of the high pressure gas pipe 407 of the use-side heat exchanger 412B and 412C are closed to switch the low pressure gas pipe 408. Open the valves 410B and 411B.

Accordingly, the refrigerant discharged from the compressor 418 flows into the refrigerant discharge tube 403, the switching valve 405A, and the heat source side heat exchanger 419 in order to liquefy condensation, and then the refrigerant flow rate control valve 417 and Via the liquid pipe 409, it is distributed to the refrigerant flow volume control valves 414, 415, 416 of each utilization side unit 401A, 401B, 401C, and is pressure-reduced here.

At this time, the microcomputer 422 opens all of the refrigerant flow rate control valves 417, while the refrigerant flow rate control valves 414, 415, and 416 are connected to the temperature sensors 423A, 423B, and 423C. The amount of reduction is adjusted according to the output. Thereafter, the refrigerant having passed through the refrigerant flow rate control valves 414, 415, and 416 flows into each of the use side heat exchangers 412A, 412B, and 412C, and evaporates and vaporizes. The low pressure gas pipe 408 enters the low pressure gas pipe 408 via the switching valves 410B and 411B, and the low pressure gas pipe 408 enters the low pressure gas pipe 408 as it is. The refrigerant joined in the low pressure gas pipe 408 is sucked into the compressor 418 sequentially through the refrigerant suction pipe 404 and the gas-liquid separator 421.

Thus, in this case, since the heat source side heat exchanger 419 acts as a condenser, and all the utilization side heat exchangers 412A, 412B, and 412C act as evaporators, the entire left chamber, solid chamber and right chamber are cooled simultaneously. In addition, as described above, the capacity of the heat source side heat exchanger 419 is approximately equal to the sum of the capacities of the entire utilization side heat exchangers 412A to 412C, and thus the use side heat exchangers 412A, 412B, and 412C serving as evaporators. The waste heat from) can be sufficiently dissipated by the heat source side heat exchanger 419.

Next, the case where the left chamber and the solid chamber are cooled while the right chamber is heated will be described.

For example, when the temperature detected by the temperature sensors 423A and 423B is equal to or higher than the cooling set temperature, the microcomputer 422 opens the switching valve 405A of the heat source side heat exchanger 419 and simultaneously opens the switching valve 405B. Close, and also close the switching valve 410A of the use-side heat exchanger 412B to cool, open the switching valve 410B, and open the switching valve 411A of the use-side heat exchanger 412C to be heated, Close the switching valve 411B.

Accordingly, a part of the refrigerant discharged from the compressor 418 sequentially passes through the refrigerant discharge pipe 403 and the switching valve 434A, and passes through the heat source side heat exchanger 419, while the remaining refrigerant passes the high pressure gas pipe 407. Through the switching valve 411A of the use side unit 401C to be heated, it flows into the use side heat exchanger 412C. The condensation liquid is then liquefied by the use side heat exchanger 412C and the heat source side heat exchanger 419. The refrigerant condensed and liquefied by these heat exchangers 412C and 419 is depressurized by the refrigerant flow rate control valves 414 and 415 of the use side units 401A and 401B via the liquid pipe 409, and then the respective use side heat exchangers. Enter 412A, 412B to evaporate and vaporize.

In addition, the microcomputer 422 uses both the refrigerant flow rate control valve 416 and the refrigerant flow rate control valve 417, and the refrigerant flow rate control valves 414 and 415 output the temperature sensors 423A and 423B. Is adjusted accordingly.

The refrigerant passing through the utilization side heat exchanger 412A flows into the low pressure gas pipe 408, and the refrigerant passing through the utilization side heat exchanger 412B passes through the switching valve 410B and flows into the low pressure gas pipe 408. The refrigerant suction tube 404 and the gas-liquid separator 421 are sequentially sucked into the compressor 418. Thus, in this case, since the use-side heat exchanger 412C acts as a condenser, the right chamber is warmed, and the left chamber and the solid chamber are cooled in the use-side heat exchangers 412A and 412B serving as the evaporator.

In such cooling and heating simultaneous operation, the refrigerant flow rate control valve 416 of the use side unit 401C is totally prevented from generating a refrigerant pressure loss. However, the microcomputer (to prevent the liquid refrigerant pressure in the liquid pipe 409 from becoming unbalanced) 422 is pressure regulated by a refrigerant flow control valve 417.

In this way, since the use side unit 401C can warm the right chamber using waste heat generated during cooling of the use side units 401A and 401B, heat recovery and use can be efficiently performed, resulting in efficient operation. I can do it. For this reason, compared with the conventional vending machine which heated only by an electric heater, electric power consumption can be reduced and operation cost can be reduced.

Next, the case where the left chamber is cooled and the solid chamber and the right chamber are heated will be described.

When the temperature detected by the temperature sensor 423A is equal to or higher than the cooling set temperature, the microcomputer 422 closes the switching valves 405A and 405B of the heat source side heat exchanger 419, and furthermore heats the using side heat exchanger. The switching valve 410A of 412B is opened, the switching valve 410B is closed, the switching valve 411A of the use-side heat exchanger 412C is opened, and the switching valve 411B is closed.

Accordingly, the refrigerant discharged from the compressor 418 is used at each switching valve 410A, 41lA of each of the use side units 401B, 401C to be heated via the refrigerant discharge pipe 403 and the high pressure gas pipe 407. It flows into heat exchanger 412B, 412C, and is condensed and liquefied in these utilization side heat exchanger 412B, 412C. The refrigerant condensed and liquefied by the use side heat exchangers 412B and 412C is decompressed by the refrigerant flow rate control valve 414 of the use side unit 401A via the liquid pipe 438, and then the use side heat exchanger 412A. Evaporated in

Further, the microcomputer 422 has all of the refrigerant flow rate control valves 415 and 416 and the refrigerant flow rate control valve 417, while the refrigerant flow rate control valve 414 is adjusted in accordance with the output of the temperature sensor 423A. .

The refrigerant passing through the use-side heat exchanger 412A flows into the low pressure gas pipe 408, and is sucked into the compressor 418 through the refrigerant suction pipe 404 and the gas-liquid separator 421. In this case, in this case, the solid chamber and the right chamber are heated in the use side heat exchangers 412B and 412C serving as the condenser, and the left chamber is cooled in the use side heat exchanger 412A serving as the evaporator.

As mentioned above, since the heating by the use side unit 401B, 401C is performed using the waste heat which arises at the time of cooling of the use side unit 401A, heat recovery and use can be performed efficiently, and efficient operation | movement can be performed. Can be.                         

Here, the respective capacity of each of the use side heat exchangers 412A, 412B, and 412C in the conventional example is the capacity (ratio 3) of the use side heat exchanger 412A = the use side heat exchanger 412B. A capacity (ratio 1) + a capacity (ratio 2) of the use-side heat exchanger 412C. As a result, the waste heat when the waste heat exchanger 412A acts as an evaporator can be used to heat the waste heat exchangers 412B and 412C, so that waste heat treatment is required using the heat source heat exchanger 419. Can be eliminated, and the waste heat recovery can be performed efficiently.

Therefore, even in this case, the power consumption can be reduced, compared to the conventional vending machine which has been heated only by the electric heater, and the operation cost can be reduced.

Here, in this type of heat pump that cools and warms using the heat of the outside air, it is known that the compressor 418 and the heat source side heat exchanger 419 are installed in the same air path and simultaneously heat exchanged with the heat radiating fan 424. When the heat source side heat exchanger 419 acts as a condenser, the compressor 418 and the heat source side heat exchanger 419 can be cooled by air simultaneously.

However, when the outside air temperature is low and the heat source side heat exchanger 419 is acting as an evaporator, the temperature of the compressor 418 is too low and the refrigerant condenses in the compressor 418 so that the refrigerant in the system is insufficient. Occurs.

Therefore, FIG. 30A and FIG. 30B show the block diagram of the conventional compressor insulation member of Unexamined-Japanese-Patent No. 8-193590. As shown to FIG. 30A and FIG. 30B, the structure which surrounds the compressor 418 with the heat insulating material 424, such as glass fiber, is proposed so that the temperature of the compressor 418 may not fall too much.

As the heat source side heat exchanger 419, a fin tube heat exchanger having high capability is used.

The heating system and the vending machine using the same include a condenser in the reservoir and an evaporator outside the reservoir,

The temperature in the reservoir is maintained at 50 to 70 ° C.

The heating system and the vending machine using the same include a condenser in the reservoir and an evaporator outside the reservoir,

The temperature in the reservoir is maintained at 50 to 70 ℃,

The commercial evaporation temperature is -10 to 10 ° C, and the commercial condensation temperature is 60 to 80 ° C.

The vending machine has a hot / cold switching room for storing goods,

A heat pump system comprising a compressor, a condenser, an expansion mechanism, and an evaporator, and heating the hot / cold switching chamber by using atmospheric heat;

A heater as a heating source which heats a hot / cold switching room simultaneously with a heat pump system,

An indoor temperature sensor that detects the indoor air temperature in the hot / cold switching room,

And a temperature adjusting control device for controlling the number of revolutions of the compressor in accordance with the comparison between the detected temperature of the room temperature sensor and the preset reference temperature.

If the detected temperature of the room temperature sensor is equal to or lower than the shift UP temperature at which the rotation speed of the compressor is increased, the compressor is increased at every shift UP waiting time, and if the detected temperature of the room temperature sensor is higher than the shift DOWN temperature, the compressor is increased every shift DOWN waiting time. Vending machine slowing down.

The vending machine has a hot / cold switching room for storing goods,

An indoor condenser installed in a hot / cold switching room,

An outdoor heat exchanger formed of a spiral fin tube installed outside a compartment for storing a product,

With compressor,

Equipped with heat dissipation fan and air path,

An outdoor heat exchanger and a heat radiating fan are arranged inside the air passage, and have a heating system.

Best Mode for Carrying Out the Invention

(Embodiment 1)

In the above conventional configuration, in order to heat the hot / cold switching chamber while cooling the cold dedicated chamber and the second cold dedicated chamber, it is necessary to simultaneously realize the condensation temperature of 60 ° C or more and the evaporation temperature of -10 ° C or less. There is a problem that a new low-temperature compressor must be developed to withstand the compression ratio condition.

Generally, refrigeration air conditioning compressors have a low temperature refrigeration compressor for a relatively low evaporation temperature of -30 to -20 ° C, a high temperature air conditioning compressor for a relatively high evaporation temperature of -10 to + 10 ° C, and intermediate evaporation. It is largely classified into a medium temperature compressor for a temperature of -20 to -10 ° C. In the vending machine where the temperature of the cold drink is 5 ° C and the temperature of the hot drink is 55 ° C, a medium temperature compressor or a low temperature compressor is used to cool the cold drink.

Moreover, since the system using these compressors is designed on the premise of heat-exchanging with normal temperature atmosphere, the use range of a compressor is normally limited to 60 degrees C or less of condensation temperature. Therefore, in order to warm the high temperature atmosphere around a hot drink, the development of the compressor which endures the condensation temperature 60-80 degreeC beyond this limit is indispensable. As a result, in order to realize cold and hot beverages in the same system, it is necessary to newly develop a compressor that can be used at an evaporation temperature of -30 ° C to -10 ° C and a condensation temperature of 60 ° C to 80 ° C.

SUMMARY OF THE INVENTION The present invention solves the conventional problems, and proposes a heating system that can be easily realized by focusing on the operating conditions of the compressor, and an object of the present invention is to provide a vending machine that can reduce the amount of power consumed during heating.

In order to solve the said conventional subject, the vending machine of this invention has the exclusive heating system which heats a hot / cold switching room separately from the cooling means of a cold exclusive room and the 2nd cold exclusive room, and this heating system Silver is provided with the high temperature | pressure receiver type compressor which uses R600a as a refrigerant | coolant, a condenser in a reservoir, and an evaporator outside a reservoir.

Accordingly, by exchanging heat with the atmosphere outside the reservoir in a specially designed storage evaporator, the compression ratio can be reduced by maintaining the evaporation temperature at a high temperature of -10 to 10 ° C, and a high temperature receiver type compressor using R600a as a refrigerant. It is possible to use the main components of the low-temperature recipro-type compressor using R134a, which is produced in large quantities, as a refrigerant, thereby ensuring durability of the compressor under severe heating conditions with an evaporation temperature of -10 to 10 ° C and a condensation temperature of 60 to 80 ° C. And high efficiency of the compressor can be easily realized.

Since the vending machine of the present invention has a dedicated heating system for heating the hot / cold switching room, it is possible to easily realize about twice the heating efficiency as compared with heating means having a heating efficiency of about 1, such as an electric heater. The power consumption of the vending machine can be greatly reduced.

As an example, for various refrigerants used in refrigeration equipment, low pressure pressure, high pressure pressure, compression ratio, discharge gas temperature, and relative values of volumetric capacity and theoretical efficiency at conditions of evaporation temperature -15 ° C / condensation temperature of 70 ° C In 1), the low pressure pressure, the high pressure pressure, the compression ratio, the discharge gas temperature, and the relative values of the volumetric capacity and the theoretical efficiency under the conditions of the evaporation temperature of 5 ° C / condensation temperature of 70 ° C are shown in Table 2. Here, the value of Table 1 and Table 2 is a calculated value in subcooling 0 degreeC, suction gas temperature of 32 degreeC, and adiabatic compression conditions. R407C in Tables 1 and 2 selects the low pressure and high pressure at which the average temperature of the liquidus and gaseous lines becomes a predetermined temperature.                     

(Table 1)

(Table 2)

As shown in Table 1, under conditions of an evaporation temperature of -15 ° C / condensation temperature of 70 ° C, when the high boiling point refrigerants R134a or R600a are used, the compression ratio exceeds 12, which causes excessive compression. It is concerned that discharge gas temperature rises abnormally under actual operating conditions and durability of a compressor falls. At the same time, when the low boiling point refrigerants R407C or R290 are used, the high-pressure pressure exceeds 2.5 MPa. Therefore, there is a concern that the load resistance of the bearing portion is insufficient, abnormal wear occurs, and the durability of the compressor decreases.                     

On the other hand, as shown in Table 2, under conditions of an evaporation temperature of 5 ° C./condensation temperature of 70 ° C., when the high boiling point refrigerants R134a or R600a are used, the compression ratio is 9 or less, and thus the normal usable range is obtained. In addition, since R600a has a smaller volume capacity and higher efficiency than R134a, it is suitable for applications requiring a small capacity and high efficiency, such as a heating system for warming a storage chamber surrounded by a heat insulating material of a vending machine. In addition, under this condensation temperature condition, when the low boiling point refrigerant | coolant R407C or R290 is used, a high pressure pressure will increase and the durability of a compressor must arise.

In addition, by using the Rishipro type compressor in which the shell is maintained at the evaporation pressure, the condensation pressure rises to a pressure equivalent to the temperature in the reservoir during the intermittent operation, which is excellent, thereby reducing the heating loss accompanying the compressor's interruption. Efficiency can be aimed at.

In addition, the present invention shortens the rise time of heating the temperature of beverage cans and the like to room temperature from room temperature to a temperature of about 55 ° C with a condensation temperature of about 80 ° C, and increases the temperature of the beverage cans and the like to about 55 ° C. When maintaining the hot temperature at, the compressor can be operated at approximately 60 ° C. with the condensation temperature at about 60 ° C., thereby reducing the heating loss associated with the intermittence of the compressor and achieving high efficiency.

The present invention is a vending machine using a heating system using an inverter compressor having a minimum heating capacity of 100 to 300 W at an evaporation temperature of 0 ° C and a condensation temperature of 60 ° C. When maintaining the temperature of the compressor, by lowering the rotational speed of the compressor to 100W to 300W, even if the compressor is operated almost continuously, it is not necessary to discharge the excess heating capacity to the outside of the reservoir, thereby achieving high efficiency.

In addition, the present invention provides a heating system in which the compressor uses R134a as a refrigerant and shares the main components with a low-temperature reciprocating compressor having a refrigeration capacity of 50 to 300 W at an evaporation temperature of -30 ° C and a condensation temperature of 40 ° C. As a used vending machine, it is possible to realize durability at high condensation temperature beyond the limit of a compressor used as an ordinary air-cooled condenser and to achieve high efficiency at the time of small capacity, and to realize a compressor with high versatility and low cost.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of the vending machine which concerns on this invention is described, referring drawings. In addition, about the structure similar to the former, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

1 is a refrigerant circuit diagram of the vending machine of Embodiment 1, FIG. 2 is a diagram showing the operating pressure range of the compressor of Embodiment 1, FIG. 3 is a diagram showing the capability of the compressor of Embodiment 1, and FIG. 4 is of Embodiment 1 The figure which shows the efficiency of a compressor and FIG. 5 is sectional drawing of the compressor of Embodiment 1. FIG.

As shown in Fig. 1, the vending machine of the present invention includes a storage chamber including a hot / cold switching chamber 101, a cold exclusive chamber 102, and a second cold exclusive chamber 103, and R600a is used as a refrigerant. , A high temperature reciprocating compressor 120, a switching chamber condenser 121 installed in the hot / cold switching chamber 101, a switching chamber evaporator 122 installed outside the storage chamber, and an expansion valve 123 for heating. It has a heating system which performs heating of the cold switching room 101 exclusively.                     

In addition, the switch room condenser 121 is a fin tube heat exchanger in the same manner as the indoor heat exchanger 104, the evaporator 105, and the second evaporator 106. The tube connection is designed so that the fin spacing and the tube spacing are relatively narrow and the flow of the refrigerant and the air flows in the opposite flow. As a result, the difference between the condensation temperature and the blowing air temperature is suppressed to about 10 ° C with a heating capacity of 200 to 300W.

On the other hand, the switching room evaporator 122 is designed in the same manner as the indoor heat exchanger 104, the evaporator 105, and the second evaporator 106 in consideration of the frost at low outside temperature.

In addition, the heating expansion valve 123 lowers the pressure of the refrigerant passing therethrough to adjust the evaporation pressure. In particular, immediately after the start of the condensation temperature not yet rising, the opening degree of the heating expansion valve 123 is increased to increase the circulation amount, whereby the rise characteristic of the condensation temperature can be improved.

Here, the high temperature receiver type compressor 120 drops the refrigerant | coolant R600a and mineral oil freezer oil into the low temperature receiver type | mold compressor used for the domestic refrigerator which uses R134a as a refrigerant. This low-temperature receiver-type compressor is driven by a DC inverter and can vary in capacity in the range of 100 to 250 W in terms of refrigeration capacity at a condensation temperature of 54.4 ° C. and an evaporation temperature of −23.3 ° C. which are standard conditions.

2 is a view showing a comparison of the operating pressure range of the compressor of the present invention and the operating pressure range of the low-temperature recipro-type compressor used in the domestic refrigerator. In Fig. 2, Conventional Example A is a low-temperature lyspro type compressor used for a domestic refrigerator using R134a as a refrigerant, and generally has a pressure range of -40 to -5 deg. C, an upper limit of 60 deg. Condensation temperature, and a compression ratio of 12 or less. Used in In addition, the conventional example B is a low-temperature recipro-type compressor used for a domestic refrigerator using R600a as a refrigerant, and as in the conventional example A, the evaporation temperature is generally -40 to -5 ° C, the upper limit of the condensation temperature is 60 ° C, and the compression ratio is 12 or less. It is used in the pressure range of. The use pressure range of the conventional example A and the conventional example B is different because the pressure at the same saturation temperature is relatively lower in R600a than in R134a.

On the other hand, as shown in Fig. 2, the high temperature receiver type compressor 120 of the present invention is used in a pressure range of the evaporation temperature -10 to +10 DEG C and the upper limit 75 DEG C of the condensation temperature, using R600a as the refrigerant. . This pressure range is within the range of the low-temperature receiver type compressor used in the domestic refrigerator using R134a shown in the conventional example A as a refrigerant, and therefore can be operated without major problems. Therefore, the high-temperature receiver type compressor 120 of the present invention uses the refrigerant R600a and the mineral oil-freezer oil in a low-temperature receiver type compressor used in a domestic refrigerator using R134a shown in the conventional example A as a refrigerant. Doing.

3 and 4 are views showing the heating capacity and the heating efficiency of the compressor of the present invention. 3 and 4 are calorie meter actual values of a single compressor at a condensation temperature of 60 ° C. Here, the cylinder volume of the compressor of the conventional example A is about 1/2 of the cylinder volume of the conventional example B, and the heating capacity and the heating efficiency of the conventional example A are nearly equivalent to the conventional example B in the same operation temperature.

As shown in Fig. 3 and Fig. 4, the heating capacity of the compressor of the present invention is about 1/2 of the compressor of the conventional example B, and at the high temperature region of the evaporation temperature of 10 to + 10 ° C., efficiency equal to or higher can be achieved. have. This is because the compressors of the conventional example A and the conventional example B are designed so that the efficiency is optimal in the low temperature region of the evaporation temperature of -30 to -15 占 폚. When the compressor of the present invention is used in a low temperature range of -30 to -15 ° C, the amount of work decreases more than the decrease of the fixed loss such as the slide loss in the bearing portion, and compared with the compressors of the conventional examples A and B. Significantly decreases the efficiency. Similarly, when the compressors of the conventional examples A and B are used in the high temperature range of -10 to + 10 ° C as they are, the work amount becomes excessive and the slide loss in the bearing increases abnormally, or the torque of the driving motor is insufficient. As a result, efficiency decreases.

Therefore, by using R134a shown in the conventional example A as a refrigerant, a low-temperature Ricpro type compressor used for a domestic refrigerator is used by dropping R600a having a small volume capability and using it at a high temperature range of -10 to + 10 ° C. A suitable amount of work can be secured for a fixed loss such as slide loss at. Thus, as shown in Figs. 3 and 4, the compressor of the present invention can achieve an efficiency equal to or higher than that of the conventional example B.

In addition, as shown in Fig. 2, since the compressor of the present invention can be used in the pressure range shown in the conventional example A, it is possible to operate without problems even at a condensation temperature of 75 to 80 deg. Warming efficiency can be maintained. In addition, at the condensation temperature of more than 80 ° C., the discharge gas temperature greatly exceeds 100 ° C., and there is a fear of thermal deterioration of the circulating refrigeration oil and the like.

5 is a cross-sectional view of the high temperature compressor 120 of the present invention.                     

As shown in FIG. 5, the high temperature compressor 120 of the present invention includes a pair of motorized elements 1105 including a refrigeration oil 1102, a stator 1103 and a rotor 1104 in a sealed container 1101. And a compression element 1106 provided on the transmission element 1105.

Next, the detailed configuration and operation of the compression element 1106 will be described below.

The crank shaft 1110 has a main shaft portion 1111 to which the rotor 1104 is press-fitted and an eccentric portion 1112 formed to be eccentric with respect to the main shaft portion 1111. The cylinder block 1120 has a compression chamber 1122 and a bearing portion 1123 supporting the main shaft portion 1111. The piston 1130 is fitted into the compression chamber 1122, and is connected to the eccentric portion 1112 by the connecting means 1131.

The capacity of the compressor is determined by the product of the rotational speed of the crankshaft 1110 and the cylinder volume. The cylinder volume is the volume in the compression chamber 1122 which the piston 1130 excludes, and is determined by the eccentric amount of the eccentric part 1112 and the outer diameter of the piston 1130. The compressor of the present invention has the same compression element and transmission element as that of the low-temperature recipro compressor used in the home refrigerator, using R134a shown in the conventional example A of FIGS. 3 and 4 as a refrigerant, and the same eccentric portion 1112 The eccentric amount and the outer diameter of the piston 1130 are comprised.

The balance weight 1133 on which the iron plates are stacked is fixed to the stator 1104. The valve plate 1135 seals the cross section of the compression chamber 1122, and the head 1136 forming the high pressure chamber is fixed to the half compression chamber 1122 side of the valve plate 1135. The suction tube 1139 is fixed to the sealed container 1101 and guides the refrigerant gas evaporated from the switching chamber evaporator 122 to the suction muffler 1140 in the sealed container 1101. The suction muffler 1140 forms a noise space 1142 to reduce noise caused by the inflow of the refrigerant gas.

The refrigerant gas introduced into the suction muffler 1140 is sucked into the compression chamber 1122 through an intake valve (not shown) fixed to the valve plate 1135, and a part of the suction muffler 1140 is sealed in a sealed container ( By communicating with 1101, the inside of the closed container 1101 is maintained at the evaporation pressure. In addition, the refrigerant gas compressed in the compression chamber 1122 flows into the head 1136 through a discharge valve (not shown) fixed to the valve plate 1135, and discharges fixed to the sealed container 1101. ) Is discharged to the switching room condenser 121 through a pipe (not shown).

The suspension spring 1150 is mounted between the snap bar 1152 fixed to the closed container 1101 and the snap bar 1153 fixed to the stator 1103 of the transmission element 1105, and the transmission element 1105. And elastically support compression element 1106 relative to closed container 1101. In addition, the electric power supplied from the commercial power source 162 is supplied to the electric element 1105 through the control circuit 161, the inverter 162, the rotor 1104 and the crankshaft 1110 of the electric element 1105. Rotate at any number of revolutions.

The operation of the vending machine of Embodiment 1 configured as described above will be described below.

When cooling the hot / cold switching room 101, after stopping the high temperature compressor 120, the compressor 108 is driven. After the refrigerant discharged from the compressor 108 is condensed in the outdoor heat exchanger 107, the refrigerant is reduced in the expansion valve A109, the expansion valve B110, and the expansion valve C111, respectively, and the switching chamber evaporator 120, The evaporator 105 is supplied to the second evaporator 106. The refrigerant evaporated in the switching chamber evaporator 120, the evaporator 105, and the second evaporator 106 is refluxed to the compressor 108.

At this time, the storage chamber that has reached a predetermined temperature in the hot / cold switching chamber 101, the cold dedicated chamber 102, and the second cold dedicated chamber 103 includes a corresponding expansion valve A109, expansion valve B110, The expansion valve C111 is closed to stop the supply of the refrigerant. In addition, when all the storage chambers reach the predetermined temperature, the operation of the compressor 108 is stopped.

Next, when the hot / cold switching chamber 101 is heated, the compressor 108 is operated while the expansion valve A109 is closed, so that the cold dedicated chamber 102 and the second cold dedicated chamber 103 are cooled. At the same time, the high temperature compressor 120 is driven. The refrigerant discharged from the high temperature compressor 120 is condensed in the switching chamber condenser 121, and then depressurized by the heating expansion valve 123 and supplied to the switching chamber evaporator 122. Then, the refrigerant evaporated in the switching chamber evaporator 122 is refluxed to the high temperature compressor 120.

At this time, for example, since the stable heat load of the hot / cold switching chamber 101 at an outside air temperature of 15 ° C. is about 100 to 200 W, the high temperature compressor 120 has an evaporation temperature of −10 to −5 ° C. and a condensation temperature. It is controlled to continuously operate at a low rotation of 42 rpm at a pressure condition of 60 to 70 ° C. This is because, if the control is performed at a higher evaporation temperature, higher efficiency can be achieved during continuous operation, but operation is performed with higher capacity than the heat load at the time of stabilization of the hot / cold switching room 101. In this case, it is necessary to intermittently operate the high temperature compressor 120, and useless operation from the standstill state until the temperature of the switching chamber condenser 121 reaches a predetermined temperature occurs, resulting in a decrease in efficiency as a whole.                     

In addition, for example, when rising to 15 degreeC of external air temperature, it is necessary to heat the hot / cold switching room 101 about 400W normally. In this case, the high temperature compressor 120 is controlled to continuously operate at a high rotation of 72 rpm under a pressure condition of an evaporation temperature of +0 to + 5 ° C and a condensation temperature of about 75 ° C. Since the temperature difference between the condensation temperature of the switching chamber condenser 121 and the indoor air is large until the temperature in the hot / cold switching chamber 101 increases, the high temperature compressor 120 also has a high capacity because a large condensation capacity can be ensured. Operation is possible.

Therefore, as the temperature in the hot / cold switching room 101 rises during the rise, the rotational speed of the high temperature compressor 120 must be lowered to 42 rpm in order to adjust the capacity. Preferably, a temperature sensor for detecting the condensation temperature of the switching chamber condenser 121 is provided, and when the condensation temperature of the switching chamber condenser 121 exceeds a predetermined value, the control for lowering the rotation speed of the high temperature compressor 120 is controlled. It is better to do it.

In addition, in this embodiment, the minimum rotation speed of the high temperature compressor 120 was 42 rpm. However, if the cylinder volume or the minimum rotational speed is selected so that the heating force at the evaporation temperature of 0 ° C / condensation temperature of 60 ° C is 100 to 300W, there is no need to interrupt the operation even when the outside temperature is 15 ° C, and efficient operation is realized. . In addition, in order to increase the heating efficiency, it is preferable to lower the minimum rotational speed and lower the heating capacity to around 100W as long as the load resistance of the bearing portion is allowed.

In the present embodiment, the refrigerant R600a and the mineral oil-based refrigeration oil are dropped as the high temperature compressor 120 into the low temperature receiver type compressor used for the domestic refrigerator using R134a shown in the conventional example A as a refrigerant. However, in accordance with the thermal properties of the refrigerant, the shape of the suction muffler, the head, the discharge valve and the suction valve can be changed. In addition, organic materials, such as insulation materials of the stator of the transmission element, can be changed in accordance with the chemical properties of the refrigerant and the refrigeration oil.

As mentioned above, in this embodiment, it can hold | maintain on high temperature conditions of the evaporation temperature -10-10 degreeC, and can reduce a compression ratio, and produce in large quantities by using the high temperature | pressure receiver type compressor which uses R600a as a refrigerant. The main components of the low-temperature recipro-type compressor using R134a as a refrigerant are useful, so it is easy to secure the durability of the compressor and to improve the efficiency of the compressor under severe heating conditions of evaporation temperature of -10 to 10 ° C and condensation temperature of 60 to 80 ° C. Can be realized.

The heating system of the vending machine according to the present invention has a high capacity and high capacity under difficult heating conditions of evaporation temperature of -10 to 10 ° C and condensation temperature of 60 to 80 ° C by using a high-temperature receiver type compressor using R600a as a refrigerant. Since the efficient heating system can be easily realized, the present invention can also be applied to applications that require saving of small-capacity heating energy, such as a show case for simultaneously storing hot and cold drinks and a cup vending machine for a small amount of hot water supply.

(Embodiment 2)

The conventional structure assumes a relatively low condensation temperature of 30 to 40 ° C., such as an air conditioner heat pump. When heating products such as canned drinks to 50 to 100 ° C., the condensation pressure becomes high, and carbonization is performed even at a high condensation pressure. In order to keep the dissolution amount of a hydrogen refrigerant low, the temperature of mineral oil type lubricating oil needs to be kept higher. As a result, the heater power required for maintaining the high-pressure shell compressor 201 at a high temperature increases, and the amount of heat leaking to the outside at the time of heating also increases, resulting in a large decrease in efficiency. In addition, when lubricating oil having a higher viscosity is used to secure the viscosity necessary for lubrication at a high temperature, the lubricating oil discharged to the system piping together with the refrigerant rises and retains an abnormal viscosity in the heat exchanger at the evaporation temperature, and the system piping is blocked. However, there is an increased risk of a secondary problem such as a lack of lubricant in the compressor.

On the other hand, it is difficult to apply the special lubricating oil, which has a small amount of dissolved hydrocarbon refrigerant, because it is expensive and does not have sufficient results.

The present invention solves the conventional problems, and proposes a cooling and heating system capable of suppressing the amount of refrigerant dissolution in the lubricating oil to be substantially constant, especially when a product such as canned beverage is heated to a high temperature of 50 to 100 ° C. An object thereof is to improve efficiency and reliability while suppressing the amount of hydrocarbon refrigerant used.

In order to solve the said conventional subject, the cooling heating system of this invention uses the low pressure shell type compressor, uses R600a as a refrigerant | coolant, and is 40 degreeC copper which is cheap and generally used as a lubricating oil of a compressor. Mineral oil or ester oil whose viscosity is 3-30 mm <2> / s is used.

As a result, by maintaining the pressure inside the compressor at a low evaporation pressure, the amount of refrigerant dissolved in the lubricating oil can be suppressed to be low, and the amount of hydrocarbon refrigerant used can be reduced. At the same time, even if the condensation temperature is 50 to 100 ° C, the hydrocarbon refrigerant R600a, which has a low condensation pressure, can be used to maintain the durability of the compressor even with a relatively small viscosity lubricant having a copper viscosity of 3 to 30 mm 2 / s at 40 ° C. Therefore, it is possible to solve the problem of reliability such as the lubricating oil remaining in the system path.

Moreover, the cooling heating system of this invention uses a low pressure shell type compressor, uses R600a as a refrigerant | coolant, surrounds a compressor with a heat insulating material, and maintains lubricating oil temperature at 40-80 degreeC at the time of heating.

Accordingly, by keeping the pressure inside the compressor at a low evaporation pressure, the amount of dissolved refrigerant in the lubricating oil is kept low, and at the time of heating when the evaporation temperature is higher than during cooling, the compressor is surrounded by a heat insulator and the lubricating oil temperature is 40 to 80 ° C. By keeping it at, it is possible to suppress the difference between the amount of refrigerant melted during cooling and heating while suppressing the amount of heat leaking to the outside. As a result, it is not necessary to always store the liquid refrigerant in order to maintain the optimum amount of refrigerant, and the minimum amount of refrigerant used can be maintained.

The cooling and heating system of the present invention suppresses the amount of the refrigerant dissolved in the lubricating oil of the compressor, thereby minimizing the amount of refrigerant used, particularly when heating products such as canned drinks to a high temperature of 50 to 100 ° C, and at the time of cooling and heating. Since the difference in the amount of refrigerant melted at the time can be suppressed, the efficiency and the reliability can be improved while suppressing the amount of the hydrocarbon refrigerant used.

According to the present invention, by keeping the pressure inside the compressor at a low evaporation pressure, the amount of refrigerant dissolved in the lubricating oil can be suppressed to be low, and the amount of hydrocarbon refrigerant used can be reduced. At the same time, even if the condensation temperature is 50 to 100 ° C, the hydrocarbon refrigerant R600a, which has a low condensation pressure, can be used to maintain the durability of the compressor even with a relatively small viscosity lubricant having a copper viscosity of 3 to 30 mm 2 / s at 40 ° C. have. Therefore, it is possible to solve the problem of reliability such as the lubricating oil remaining in the system path.

In addition, the present invention can reduce the amount of refrigerant dissolved in the lubricating oil to be low by keeping the pressure inside the compressor at a low evaporation pressure, thereby reducing the amount of hydrocarbon refrigerant used. At the same time, even if the condensation temperature is 50 to 100 ° C, the hydrocarbon refrigerant R600a, which has a low condensation pressure, can be used to maintain the durability of the compressor even with a relatively small viscosity lubricant having a copper viscosity of 3 to 30 mm 2 / s at 40 ° C. have. Therefore, it is possible to solve the problem of reliability such as the lubricating oil remaining in the system path. In addition, by using ester oil having a large saturated dissolved amount of water, the risk of moisture choke during cooling is eliminated, so that the drier in which the liquid refrigerant resides can be omitted, and as a result, the amount of refrigerant used can be further reduced.

The present invention suppresses the amount of refrigerant dissolved in lubricating oil by keeping the pressure inside the compressor at a low evaporation pressure, and at the time of heating when the evaporation temperature is higher than that of cooling, the compressor is surrounded by a heat insulating material and the lubricating oil temperature is 40 to 80 ° C. By keeping it at, it is possible to suppress the difference between the amount of refrigerant melted during cooling and heating while suppressing the amount of heat leaking to the outside. As a result, it is not necessary to always store the liquid refrigerant in order to maintain the optimum amount of refrigerant, so that the minimum amount of refrigerant used can be maintained.

In addition, the present invention provides a liquid refrigerant dissolved in the compressor to be quickly supplied to the system by heating the heater while the evaporation temperature is higher than the cooling time, while the compressor is started and warmed up until the temperature is still increased. Increase the system's operating characteristics.

Moreover, this invention can improve compressor efficiency by reducing the temperature of a compressor at the time of cooling which evaporation temperature becomes low compared with the case of heating.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of the vending machine which concerns on this invention is described, referring drawings. In addition, about the structure similar to the former, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

6 is a refrigerant circuit diagram of a cooling heating system according to the second embodiment. Fig. 7 is a diagram showing the characteristics of the amount of refrigerant dissolved in oil of the mineral oil A of the embodiment. 8 is a diagram showing the characteristics of the oil viscosity of the mineral oil A of the embodiment. 9 is a diagram showing the characteristics of the amount of refrigerant dissolved in oil of the mineral oil (B) of the embodiment. It is a figure which shows the characteristic of the oil viscosity of the mineral oil B of the same embodiment.

As shown in FIG. 6, the cooling heating system of the present invention uses isobutane, which is a hydrocarbon refrigerant, and at the same time, a low pressure shell compressor 220, a four-way valve 202, an accumulator 203, and an outdoor heat exchanger 204. The indoor heat exchanger 205 has a basic configuration. When the room is cooled, the refrigerant discharged from the low pressure shell type compressor 220 switches the flow path to the four-way valve 202, is supplied from the outdoor heat exchanger 204 to the indoor heat exchanger 205, and the four-way valve 202 is again supplied. It is refluxed from the accumulator 203 to the low pressure shell compressor 220 via. At the same time, when the room is warmed, the refrigerant discharged from the low pressure shell type compressor 220 switches the flow path to the four-way valve 202, and is supplied from the indoor heat exchanger 205 to the outdoor heat exchanger 204, and again the four-way valve. Reflow from the accumulator 203 to the low pressure shell compressor 220 via 202.

Here, generally, the indoor heat exchanger 205 is installed in a storage compartment in which objects to be cooled and warmed, such as canned beverages, are stored, and at the same time, the low pressure shell compressor 220, the four-way valve 202, the accumulator 203, and the outdoor heat exchanger are provided. 204 is disposed outside the storage chamber.

In addition, the piping connecting the outdoor heat exchanger 204 and the indoor heat exchanger 205 includes a heating capillary tube 206, a cooling check valve 207, a cooling capillary tube 208, and a heating check valve. The valve 209 and the dryer 210 are connected. Here, the heating capillary tube 206, the cooling check valve 207, the cooling capillary tube 208, and the heating check valve 209 are connected in parallel, respectively, and the heating capillary tube 206 is connected. ) And a dryer 210 at a position fitted to the cooling capillary tube 208. In addition, in general, the outdoor heat exchanger 204 and the indoor heat exchanger 205 are each blown with an independent blower fan (not shown) as needed to promote air cooling and heat exchange.

Here, the low pressure shell compressor 220 is surrounded by a cover 221 made of a heat insulating material, and a heater 223 for heating the sensor 222 for measuring the temperature inside the cover 221 and the low pressure shell compressor 220. And a fan 224 that receives outside air in the cover 221.

The operation of the cooling heating system of the present invention configured as described above will be described below.

When the inside of the storage chamber is cooled, the refrigerant discharged from the low pressure shell-type compressor 220 switches the flow path to the four-way valve 202 and is supplied to the outdoor heat exchanger 204 to liquefy condensation. The liquid refrigerant from the outdoor heat exchanger 204 is supplied to the dryer 210 via the cooling check valve 207. Then, the liquid refrigerant from the dryer 210 is depressurized by the cooling capillary tube 208 and is supplied to the indoor heat exchanger 205 to evaporate and vaporize, and the gas refrigerant is again passed through the four-way valve 202 to accumulator 203. Reflux from the low pressure shell compressor (220).

In addition, when the inside of the storage chamber is warmed, the refrigerant discharged from the low-pressure shell-type compressor 220 switches the flow path to the four-way valve 202 and is supplied to the indoor heat exchanger 205 to condense and liquefy. The liquid refrigerant from the indoor heat exchanger 205 is supplied to the dryer 210 via the heating check valve 209. Then, the liquid refrigerant from the dryer 210 is depressurized by the heating capillary tube 206 and is supplied to the outdoor heat exchanger 204 to vaporize, and the gas refrigerant is again passed through the four-way valve 202 to accumulator 203. Reflux from the low pressure shell compressor (220).

Here, with reference to FIG. 7 and FIG. 8, the refrigerant | coolant melt | dissolution amount characteristic and oil viscosity characteristic of mineral oil A which are the lubricating oil stored in the inside of the low pressure shell type compressor 220 are demonstrated below.

As shown in FIG. 7, the weight% of the refrigerant contained in the mixture of the mineral oil A and the refrigerant (hereinafter referred to as the amount of refrigerant dissolved in the oil) is the temperature of the mineral oil A (hereinafter referred to as oil temperature). And the refrigerant pressure inside the low-pressure shell compressor 220 (which is converted into a saturation temperature, hereinafter referred to as a saturation temperature of the refrigerant). In particular, when the difference between the saturation temperature and the oil temperature of the refrigerant decreases, the amount of refrigerant dissolved in the oil rapidly increases. In general, it is known to show the same tendency in the combination of hydrocarbon refrigerant and mineral oil. In addition, from the viewpoint of suppressing the amount of hydrocarbon refrigerant used, the amount of refrigerant dissolved in oil is preferably 0 to 5% by weight.

As shown in Fig. 8, the kinematic viscosity (hereinafter referred to as oil viscosity) of the mixture of mineral oil A and the refrigerant also varies greatly with the oil temperature and the saturation temperature of the refrigerant. The oil viscosity drops rapidly as the saturation temperature of the refrigerant rises at the oil temperature of 40 ° C., because the amount of refrigerant dissolved in the oil increases rapidly. In general, it is known to show the same tendency in the combination of hydrocarbon refrigerant and mineral oil. In addition, the oil viscosity is preferably 3 to 10 mm 2 / s from the viewpoint of ensuring durability of the compressor and reducing the loss due to the viscosity resistance of the lubricating oil.

In the present embodiment, when the inside of the storage chamber is cooled, the condensation temperature of the outdoor heat exchanger 204 is slightly higher than the outside air temperature at 20 to 50 ° C., and the evaporation temperature of the indoor heat exchanger 205 is considered to be freezing to refrigeration. It becomes -30-10 degreeC. On the other hand, when the inside of the storage chamber is warmed, the evaporation temperature of the outdoor heat exchanger 204 is -10 to 10 ° C equivalent to that of a general heat pump air conditioner, and the condensation temperature of the indoor heat exchanger 205 is a product holding temperature 50 such as canned beverage. Considering -60 degreeC, it will be 50-70 degreeC.

As a result, when the inside of the storage chamber is cooled, the saturation temperature of the refrigerant is -30 to -10 ° C, so that the amount of refrigerant melted in the oil and the viscosity of the oil are appropriate within the range where the oil temperature does not exceed 80 ° C. Able to know. Therefore, since the discharge gas temperature is suppressed low by using R600a having a low refrigerant pressure, the fan 224 may be driven to the extent that the low pressure shell compressor 220 and the oil temperature are vented in the cover 221 without significantly increasing the oil temperature. .

In addition, when the outside air temperature is low and the condensation temperature is low, since the low pressure shell compressor 220 and the oil temperature do not rise and do not need to drive the fan 224, the ambient temperature of the low pressure shell compressor 220 is measured by the sensor 222. It is preferable to drive the fan 224 when the value exceeds a predetermined value while measuring with.

On the other hand, when the inside of the storage chamber is warmed, since the saturation temperature of the refrigerant is -10 to + 10 ° C, it is understood that the oil temperature needs to be maintained at 40 to 80 ° C or more in order to appropriately suppress the amount of refrigerant dissolved in the oil. have. In addition, when it exceeds 80 degreeC, since an oil viscosity falls below an appropriate value, it turns out that oil temperature must be controlled in narrow range according to evaporation temperature. Thus, the low-pressure shell compressor 220 is surrounded by a cover 221, and the ambient temperature of the low-pressure shell compressor 220 is measured by the sensor 222. When the value falls below a predetermined value, the heater 223 is energized. The oil temperature of the low pressure shell compressor 220 is maintained at 40-80 degreeC or more. In particular, since the oil temperature is low at the time of start-up, it is preferable to continuously energize the heater 223 to quickly increase the temperature.

In addition, the calorific value of the low-pressure shell compressor 220 is proportional to the amount of work. Therefore, if the condensation temperature of the indoor heat exchanger 205 is almost fixed when the inside of the storage chamber is warmed, the outdoor heat exchanger 204 is only surrounded by the cover 221 made of a heat insulating material. When the evaporation temperature of -10 to + 10 ° C is low, the temperature of the lubricating oil decreases, and when high, the temperature of the lubricating oil rises, thereby showing a tendency to maintain the oil temperature almost appropriately. Therefore, if the heat insulation characteristic of the cover 221 is properly adjusted, the energization of the heater 223 can be made almost zero.

Here, FIG. 9 and FIG. 10 show the effect of using a mineral oil (B) having a copper viscosity of 40 ° C. of about 30 mm 2 / s instead of a mineral oil (A) having a viscosity of 40 ° C. of about 10 mm 2 / s. It demonstrates below, referring. In addition, description is abbreviate | omitted about the same term as FIG.7 and FIG.8.

As shown in FIG. 9, the characteristic of the amount of refrigerant | coolant melt | dissolution in the oil of mineral oil B shows the tendency which does not have a big difference with the mineral oil A shown in FIG. In addition, from the viewpoint of suppressing the amount of hydrocarbon refrigerant used, the amount of refrigerant dissolved in oil is preferably 0 to 5% by weight.

As shown in FIG. 10, the absolute value of the oil viscosity changes as compared to the mineral oil A shown in FIG. 8 in the characteristic of the oil viscosity of the mineral oil B, and it is understood that the change tendency is the same. As a result, from the viewpoint of securing the durability of the compressor and reducing the loss due to the viscosity resistance of the lubricating oil, the oil temperature can be controlled higher than that of the mineral oil (A) in order to maintain an appropriate oil viscosity of 3 to 10 mm 2 / s. There is a need.

In the present embodiment, when mineral oil B is used instead of mineral oil A, when the inside of the storage chamber is cooled, the saturation temperature of the refrigerant is -30 to -10 ° C, so that the oil temperature is 70 to 120 to maintain an appropriate oil viscosity. It turns out that it is necessary to keep it at ° C. Therefore, when the cover 221 made of a heat insulating material is thickened to increase the heat insulating performance, or when the low pressure shell compressor 220 having a small outer surface area and a relatively high temperature is selected, the amount of refrigerant in oil and the amount of refrigerant in oil that are appropriate in the present embodiment are improved. Viscosity can be realized.

Similarly, in the case of heating the inside of the storage chamber, it can be seen that the oil temperature may be maintained at 70 to 120 ° C. in order to maintain an appropriate viscosity. This is because even if the saturation temperature of the refrigerant is -10 to + 10 ° C, the amount of refrigerant dissolved in oil is appropriate when the oil temperature is maintained at 40 to 80 ° C or more.

However, if the oil temperature control target for cooling and warming the inside of the storage chamber is too high, if the initial oil temperature is low, such as at the start of the low-pressure shell compressor 220, the time until the oil temperature reaches the target value and operates properly is long. There is a problem. For example, since the electric power is consumed by continuously energizing the heater 223 for a long time, the upper limit of the control target of oil temperature is preferably about 80 ° C. Therefore, in the low pressure shell type compressor 220, it is better to use mineral oil whose 40 degreeC dynamic viscosity is about 3-30 mm <2> / s, Preferably it is about 10 mm <2> / s.

In the present embodiment, when the high pressure shell compressor 201 is used in place of the low pressure shell compressor 220, the saturation temperature of the refrigerant becomes 20 to 50 ° C. during cooling and 50 to 70 ° C. during heating. As can be seen from FIG. 9, a higher oil temperature above 120 ° C. is required. 8 and 10, in order to obtain an appropriate oil viscosity at a higher oil temperature above 120 ° C., it is necessary to use a high viscosity mineral oil, and there is a fear of returning oil from the heat exchanger which becomes the evaporation temperature. do. In particular, it is more difficult to maintain the amount of refrigerant dissolved in oil at an appropriate value of 0 to 5% by weight, and to suppress the amount of refrigerant used, corresponding to the saturation temperature of 50 to 70 ° C of the refrigerant during heating. Therefore, it is necessary to apply a special lubricating oil having a small amount of dissolved hydrocarbon refrigerant, and it is difficult to put practical use due to its price and lack of performance.                     

In addition, in this embodiment, instead of mineral oil (A) and mineral oil (B), it is also possible to use ester oil whose copper viscosity of 40 degreeC is about 3-30 mm <2> / s. For example, ester oils composed of hindered esters using polyhydric alcohols such as pentaerythritol and neopentyl glycol, which are generally used as lubricating oils for refrigerators using R134a, are relatively inexpensive and have practical use. to be. Since such ester oil shows the dissolution amount of the hydrocarbon refrigerant similar to mineral oil, it can be used similarly to mineral oil. In addition, since the amount of water dissolved is several ten times higher than that of mineral oil, such ester oil is characterized by no moisture choke and can be operated without a dryer. As a result, it is possible to reduce by the amount of hydrocarbon refrigerant remaining in the dryer.

As mentioned above, since the cooling heating system which concerns on this invention can suppress the refrigerant dissolution amount in lubricating oil substantially uniformly especially when goods, such as canned drinks, are heated at high temperature of 50-100 degreeC, it is a showcase, food storage, etc. In a cooling heating system which alternates cooling and heating, the present invention can also be applied for the purpose of improving efficiency and reliability while suppressing the amount of hydrocarbon refrigerant used.

Next, in the above conventional configuration, in order to heat the hot / cold switching room mainly by using the heat pump system, a heat pump system having a surplus heating capacity in consideration of the load fluctuation is required, and at the same time the overheating of the indoor heat exchanger There is a problem that fluctuations in room temperature occur and the temperature of products such as canned drinks cannot be maintained with high accuracy.

In general, the heating load of the hot / cold switching room of the vending machine increases by 2 to 3 times with respect to the stable load. Therefore, when only the heater is used, the heating capacity of the hot / cold switching room is adjusted to the maximum load. On / off is repeated every 10 to 20 minutes to continuously change the heating ability of the time average from 0% to 100%, thereby responding to the load variation.

Similarly, when a hot / cold switch chamber is heated mainly using a heat pump system, for example, a heat pump system having a heating capacity that can withstand about 2 times the load fluctuation with respect to a stable load is provided. Repeatedly responds to the load fluctuations, and supplements the heating capacity that is insufficient at the maximum load, for example, equivalent to 1 times the load at rest, with an auxiliary heater, and provides about 3 times the maximum capacity for the load at rest. Will be exercised.

By the way, if the goods storage room is kept warm by a heat insulating material like a vending machine, the load fluctuation by the outside air temperature is very small, and the maximum load is rarely generated when goods are added. Therefore, when the hot / cold switching room is mainly heated by using a heat pump system, the capacity is almost always adjusted while repeating the increase and decrease of the compressor frequently, and the fluctuation of the room temperature due to the overheating of the indoor heat exchanger occurs, and the canned beverage There is a problem that the temperature of such products cannot be maintained with high accuracy.

In addition, the room temperature at the time of heating of the hot / cold switching room is about 55 ° C., which is considerably higher than that of the heat pump system used in a general air-conditioning unit, so that the condensation temperature of the indoor heat exchanger may rise excessively and impair the durability of the compressor. There is this. Therefore, there is a need to apply a high capacity indoor heat exchanger, but when the maximum capacity of the heat pump system increases, the problem arises that the indoor heat exchanger becomes large and the installation in the goods storage chamber becomes difficult.

In addition, when the cold dedicated chamber is used as a heat source and the cooling of the cold dedicated chamber and the heating of the hot / cold switching chamber are simultaneously realized, if the cooling of the cold dedicated chamber is completed first during the heating of the hot / cold switching chamber, Since heating cannot be continued, a problem arises that the configuration and control of the heat pump system becomes more complicated.

The present invention solves the conventional problems, proposes a configuration in which the heat pump system can be used more normally in view of the load fluctuation of the vending machine, and can suppress the fluctuation of the room temperature caused by the overheating of the indoor heat exchanger. Provide vending machines.

In the third and fourth embodiments of the present invention, in order to solve the above-mentioned conventional problems, the vending machine of the present invention is designed so that the heating capacity of the heat pump system is equal to or less than the heating capacity of the heater, so that the load at the time of stable The heating capacity of the heat pump system is adjusted so as not to exceed greatly.

As a result, the heat pump system can be stably operated while maintaining a constant speed at or below the required capability, thereby suppressing fluctuations in the room temperature due to overheating of the indoor heat exchanger.

The vending machine of the present invention designs the heating capacity of the heat pump system to be equal to or less than the heating capacity of the heater, and adjusts the heating capacity of the heat pump system so as not to significantly exceed the load at stable, thereby overheating the indoor heat exchanger. It is possible to suppress the fluctuations in room temperature accompanied by the temperature and to maintain the temperature of products such as canned drinks with high accuracy. As a result, even in the case of using a small and small capacity heat exchanger in accordance with the stable heating capability, the durability of the compressor can be ensured.

The present invention has a small heating capability of the heat pump system, can suppress fluctuations in the room temperature of the hot / cold switching room accompanying overheating of the indoor heat exchanger, and can maintain the temperature of goods such as canned beverages with high accuracy. As a result, the durability of the compressor can be ensured even when a small and small indoor heat exchanger that is adapted to a stable heating capacity is used.

Moreover, especially this invention can suppress the overheating of the indoor heat exchanger which arises by operating a compressor at high speed continuously until the room temperature of a hot / cold switching room rises especially in an initial starting state.

In addition, the present invention sets the minimum heating capacity of the heat pump system to be slightly smaller than the heating load of the hot / cold switching room and suppresses the room temperature of the hot / cold switching room from dropping too much, thereby reducing the temperature of goods such as canned beverages. Maintain high precision.

Moreover, this invention can temperature-adjust with a heater which can continuously change a capacity, heating continuously by heating a heat pump system, and can maintain the temperature of goods, such as canned drinks, with high precision.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of the vending machine which concerns on this invention is described, referring drawings. In addition, about the structure similar to the former, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

(Embodiment 3)                     

11 is a refrigerant circuit diagram of the vending machine according to the third embodiment, and FIG. 12 is a heating control timing chart of the vending machine according to the third embodiment.

As shown in FIG. 11, the vending machine of the present invention includes a storage chamber including a hot / cold switching chamber 301, a cold dedicated chamber 302, and a second cold dedicated chamber 303, and a heating compressor 320. ), A switching room condenser 321 installed in the hot / cold switching room 301, a switching room evaporator 322 installed outside the storage room, an expansion valve 323 for heating, and heating of the hot / cold switching room 301. It has a heat pump system which performs exclusively.

In addition, in order to complement the heating capability of the heat pump system, a heater 324 made of an electric heater having a heating capability almost equivalent to the maximum heating capability of the heat pump system is provided under the wind of the switching room condenser 321. The air warmed by the switching chamber condenser 321 and the heater 324 is blown by the heating fan 325 to circulate the interior of the hot / cold switching chamber 301. Here, the heating compressor 320 and the heater 324 are temperature control controllers (shown in accordance with the comparison between the room temperature sensor 326 that measures the room temperature of the hot / cold switching room 301 and a predetermined reference value). Not controlled).

The operation of the vending machine according to the third embodiment configured as described above will be described below.

When the hot / cold switching room 301 is cooled, the compressor 308 is driven after stopping the heating compressor 320. The refrigerant discharged from the compressor 308 is condensed in the outdoor heat exchanger 307, and then reduced in pressure by the expansion valve A309, the expansion valve B310, and the expansion valve C311, respectively, and the switching room evaporator 320. To the evaporator 305 and the second evaporator 306. The refrigerant evaporated in the switching room evaporator 320, the evaporator 305, and the second evaporator 306 is refluxed to the compressor 308.

At this time, the storage chamber that has reached a predetermined temperature in the hot / cold switching chamber 301, the cold dedicated chamber 302, and the second cold dedicated chamber 303 has a corresponding expansion valve A309, expansion valve B310, and expansion. The valve C311 is closed to stop the supply of the refrigerant. In addition, when all the storage chambers reach the predetermined temperature, the operation of the compressor 308 is stopped.

Next, when the hot / cold switching chamber 301 is warmed, the compressor 308 is operated while the expansion valve A309 is closed to cool the cold dedicated chamber 302 and the second cold dedicated chamber 303. At the same time, the heating compressor 320 is driven. The refrigerant discharged from the heating compressor 320 is condensed in the switching chamber condenser 321, and then depressurized by the heating expansion valve 323 and supplied to the switching chamber evaporator 322. Then, the refrigerant evaporated in the switching room evaporator 322 is refluxed to the heating compressor 320.

Next, the change of the rotation speed of the heating compressor 320 and the ON / OFF state of the heater 324 with respect to the room temperature change of the hot / cold switching room 301 at the time of heating is explained in detail using FIG. Explain.

12 is a time chart in which time divisions t0 to t27 are taken along the horizontal axis, changes in the room temperature of the hot / cold switching chamber 301 in order from above, changes in the condensation temperature of the switching chamber condenser 321, and heater 324. The total sum of the heating capacity of the heat pump system including the ON / OFF state, the rotation speed of the heating compressor 320, the heater 324, the heating compressor 320, and the like is shown. In addition, T0 described on the vertical axis of room temperature is the ambient temperature, T1 is the heater ON temperature which is a reference to put the heater 324, heater OFF temperature which is the reference which cuts the heater 324, and T2 is the temperature of the compressor 320 for heating. The shift UP temperature, T3, which is a reference for increasing the rotational speed, indicates a shift DOWN temperature, which is a reference for reducing the rotational speed of the heating compressor 320. In addition, Tp described on the vertical axis of the condensation temperature is the target temperature at the time of warming of the product stored in the hot / cold switching room 301, and Tq is the upper limit condensation desirable in securing the reliability of the heating compressor 320. Indicates the temperature.

Here, the heater 324 turns ON when the room temperature becomes lower than the heater ON temperature, and turns OFF when the heater 324 becomes equal to or higher than the heater OFF temperature. In addition, the warming compressor 320 increases the rotational speed in the order of N1, N2, N3, N4 when the room temperature is lower than the shift UP temperature, and increases the rotational speed of N4, N3, N2, N1 when the temperature is lower than the shift-down temperature. Decelerate in order. In addition, the heating compressor 320 decelerates when the condensation temperature of the switching chamber condenser 321 exceeds the upper limit condensation temperature Tq after a predetermined time after changing the rotation speed.

In general, in the warming compressor 320 having a compression mechanism of the receiver type, the minimum rotational speed N1 is about 20 to 30 rpm, and the ratio of the minimum rotational speed N1 and the highest rotational speed N4 is set to about one to three to four. As such, changing the rotational speed of the heating compressor 320 discontinuously is particularly important for equipment installed indoors such as vending machines, in order to avoid abnormal vibration or noise caused by resonating at a specific rotational speed. Do.

In FIG. 12, the time t0 is an initial starting state in which the room temperature has dropped to near the outside temperature T0, and the heater 324 is turned ON because the room temperature is lower than T1. In addition, the warming compressor 320 is operated at the highest rotation speed N4. This is because a large heating capacity is required in the initial starting state, and thus the initial starting state is detected from the power-on or door opening and closing, and the heating compressor 320 is forcibly operated at the highest rotation speed N4.

Then, when the room temperature exceeds T1 at the time t3, the heater 324 is turned off. When the condensation temperature exceeds Tq at the time t6, the heating compressor 320 is sequentially decelerated from N4 to N1. The condensation temperature does not fall in the section of time t6 at the time t6 because the heating compressor 320 has been operated for a long time at the maximum rotation speed N4 in the initial starting state, so that the switching room condenser 321 and its peripheral members are overheated. This is because the temperature of the peripheral member does not decrease rapidly even if the rotation speed of the heating compressor 320 is gradually lowered.

Then, by maintaining the compressor 308 at the minimum rotational speed N1 in the interval between the times t8 and t18, the room temperature gradually decreases, and if the room temperature falls below T2 at the time t19, the heating compressor 320 is sequentially rotated from the rotational speed N1 to N4. Going up. As a result, the condensation temperature of the switching chamber condenser 321 rises again, and the warming ability increases, and the room temperature rises again after the time t22.

After that, when the condensation temperature exceeds Tq, the heating compressor 320 is gradually decelerated, and when the room temperature is lower than T2, the heating compressor 320 is sequentially increased in order to stabilize the room temperature. In addition, when the heating load is small when the outside temperature is high, even if the heating compressor 320 is operated at the minimum rotation speed N1, the room temperature rises further than T3 to exceed the upper limit temperature (not shown) of the room temperature, or the rotation speed If the condensation temperature exceeds Tq after a predetermined time after the change, the heating compressor 320 stops operating.

In this way, when the condensation temperature exceeds the upper limit temperature Tq, control is performed to sequentially decelerate the heating compressor 320, thereby suppressing the switching chamber condenser 321 and its peripheral members from continuously exceeding the upper limit temperature Tq. As a result, fluctuations in the room temperature caused by the excessively high temperature of the switching room condenser 321 can be suppressed, and the temperature of goods such as canned drinks can be maintained with high accuracy.

In addition, by designing the maximum heating capacity of the heat pump system to be equal to the heating capacity of the heater, while suppressing overheating of the switching chamber condenser 321 when the heating compressor 320 continuously operates at the highest rotational speed, The amount of change in the heating capacity due to the change in rotational speed becomes small, and a smooth change in the room temperature of the hot / cold switching room 301 can be realized.

In addition, by using a heat pump system that independently heats the hot / cold switching chamber 301 using the outside air as a heat source, the cooling load of the cold exclusive chamber 302 and the second cold exclusive chamber 303 is not changed. The heating ability is stable, and a change in room temperature of the hot / cold switching room 301 can be realized more smoothly.

In addition, a time interval for sequentially increasing or decreasing the heating compressor 320 sequentially, that is, a waiting time from changing the rotational speed of the heating compressor 320 to performing the next change is provided for several minutes to several ten minutes. It is preferable. Even if the rotation speed of the heating compressor 320 is rapidly increased or decelerated, the heating capacity cannot be changed rapidly. If the rotation speed of the heating compressor 320 is rapidly changed after the room temperature is stabilized, the switching room condenser 20 is overheated. The temperature is increased, rather increasing the fluctuation of room temperature.

Moreover, it is preferable to set also the shortest waiting time when the condensation temperature of the switching room condenser 321 exceeds the upper limit condensation temperature Tq and decelerates the heating compressor 320 to several minutes to several ten minutes. This causes the warming compressor 320 to be decelerated forcibly regardless of the room temperature. Therefore, if this waiting time is small, it is possible to reduce the durability of the warming compressor 320 by repeating the increase and decrease frequently.

(Fourth Embodiment)

FIG. 13 is a refrigerant circuit diagram of the vending machine of the fourth embodiment, and FIG. 14 is a timing chart of the heating control of the vending machine of the fourth embodiment.

As shown in FIG. 13, the vending machine of the present invention includes a storage chamber including a hot / cold switching chamber 301, a cold dedicated chamber 302, and a second cold dedicated chamber 303, and has a heating compressor 320. ), A switching room condenser 321 installed in the hot / cold switching room 301, a switching room evaporator 322 installed outside the storage room, an expansion valve 323 for heating, and heating of the hot / cold switching room 301. It has a heat pump system dedicated to this.

In addition, in order to complement the heating capability of the heat pump system, a heater 324 made of an electric heater having a heating capability almost equivalent to the maximum heating capability of the heat pump system is provided under the wind of the switching room condenser 321. The air warmed by the switching chamber condenser 321 and the heater 324 is blown by the heating fan 325 to circulate the interior of the hot / cold switching chamber 301. Here, the heating compressor 320 is connected to a control device for temperature adjustment (not shown) in accordance with the comparison between the room temperature sensor 326 which measures the room temperature of the hot / cold switching room 301 and a preset reference value. Controlled by Moreover, the heater 324 is a control apparatus for temperature adjustment according to the comparison with the blowing air temperature sensor 330 which measures the temperature of the blowing air warmed by the switching room condenser 321 and the heater 324, and a preset reference value. (Not shown).

The operation of the vending machine according to the fourth embodiment configured as described above will be described below.

In the case of cooling the hot / cold switching room 301, the compressor 308 is driven after stopping the heating compressor 320. The refrigerant discharged from the compressor 308 is condensed in the outdoor heat exchanger 307, and then depressurized by the expansion valve A309, the expansion valve B310, and the expansion valve C311, respectively, and the switching chamber evaporator 320, Evaporator 305 is supplied to the second evaporator 306. The refrigerant evaporated in the switching room evaporator 320, the evaporator 305, and the second evaporator 306 is refluxed to the compressor 308.

At this time, the storage chamber that has reached a predetermined temperature in the hot / cold switching chamber 301, the cold dedicated chamber 302, and the second cold dedicated chamber 303 includes a corresponding expansion valve A309, expansion valve B310, The expansion valve C311 is closed to stop the supply of the refrigerant. In addition, the compressor 308 stops operation when all the storage chambers reach the predetermined temperature.

Next, when the hot / cold switching chamber 301 is warmed, the compressor 308 is operated while the expansion valve A309 is closed to cool the cold dedicated chamber 302 and the second cold dedicated chamber 303. At the same time, the heating compressor 320 is driven. The refrigerant discharged from the heating compressor 320 is condensed in the switching chamber condenser 321, and then decompressed by the heating expansion valve 323 and supplied to the switching chamber evaporator 322. Then, the refrigerant evaporated in the switching room evaporator 322 is refluxed to the heating compressor 320.

Next, the change of the rotation speed of the heating compressor 320 and the ON / OFF state of the heater 324 with respect to the room temperature change of the hot / cold switching room 301 at the time of heating is explained in detail using FIG. Explain.

Fig. 14 is a time chart in which time divisions t0 to t27 are taken along the horizontal axis, and the change in the room temperature of the hot / cold switching chamber 301 in order from the top, the condensation temperature (solid line) of the switching chamber condenser 321 and the heater ON are shown. The heating capability of the heat pump system which consists of a change of blown air temperature (a dashed-dotted line), the ON / OFF state of the heater 324, the rotation speed of the heating compressor 320, the heater 324, the heating compressor 320, etc. Displays the total sum of. In addition, T0 described on the vertical axis of room temperature is the outside temperature, T2 is the shift UP temperature which is a reference for increasing the rotation speed of the heating compressor 320, and T3 is the reference for reducing the rotation speed of the heating compressor 320. Indicates the shift down temperature. Moreover, shift DOWN temperature which is a reference | standard which slows down condensation rotation speed is shown. In addition, Tp described on the vertical axis of the condensation temperature is a target temperature at the time of heating of the product stored in the hot / cold switching chamber 301, and Tq is a condensation temperature of the upper limit which is preferable in securing the reliability of the heating compressor 320. Indicates.

Here, the warming compressor 320 increases the rotational speed in the order of N1, N2, N3, N4 when the room temperature is lower than the shift UP temperature, and increases the rotational speed of N4, N3, N2, N1 when the temperature is lower than the shift-up temperature. Decelerate in order. In addition, the heating compressor 320 decelerates when the condensation temperature of the switching chamber condenser 321 exceeds the upper limit condensation temperature Tq after a predetermined time after changing the rotation speed.

On the other hand, the heater 324 turns on when the jet air temperature detected by the jet air temperature sensor 330 becomes lower than the upper limit temperature Tq of the condensation temperature, and turns off when the heater 324 becomes higher than the upper limit temperature Tq of the condensation temperature. This means that the heating capacity is adjusted so that the temperature of the blowing air warmed by the switching chamber condenser 321 and the heater 324 becomes approximately constant in the vicinity of Tq. In addition, since the temperature of the blowing air when the heater 324 is turned off is almost the same as the condensing temperature of the switching chamber condenser 321, the actual blowing air temperature is the condensing temperature of the switching chamber condenser 321 shown in FIG. 14. It fluctuates minutely between (solid line) and blown air temperature (single chain line) at the heater ON.

In general, in the warming compressor 320 having a compression mechanism of the receiver type, the minimum rotational speed N1 is about 20 to 30 rpm, and the ratio of the minimum rotational speed N1 and the highest rotational speed N4 is set to about one to three to four. As such, changing the rotational speed of the heating compressor 320 discontinuously is particularly important for equipment installed indoors such as vending machines, in order to avoid abnormal vibration or noise caused by resonating at a specific rotational speed. Do.

In FIG. 14, the time t0 is an initial starting state in which the room temperature has dropped to near the outside temperature T0, and the heater 324 is turned ON because the blown air temperature is lower than Tq. In addition, the warming compressor 320 is operated at the highest rotation speed N4. This is because a large heating capacity is required in the initial starting state, and thus the initial starting state is detected from the power-on or door opening and closing, and the heating compressor 320 is forcibly operated at the highest rotation speed N4.                     

Then, when the blowing air temperature exceeds Tq at time t3, the heater 324 is finely turned on and off, while adjusting the blowing air temperature to be approximately constant at Tq while increasing the ratio of OFF time with the increase of the condensation temperature. do.

In addition, when the condensation temperature exceeds Tq at time t6, the heater 324 is turned off completely, and the heating compressor 320 sequentially decelerates from the rotational speed N4 to N2. The reason why the heating compressor 320 does not decelerate from N2 to N1 is because the minimum rotational speed of the heating compressor 320 is set to N2. This estimates the load of the hot / cold switching chamber 301 from the ambient temperature and the temperature setting of the second cold exclusive chamber 303, and compares the minimum rotational speed with the heating capacity of each rotational speed of the heating compressor 320. This is the result of applying the control to decide. In this case, since the load of the hot / cold switching chamber 301 estimated from the ambient temperature and the temperature setting of the second cold exclusive chamber 303 is greater than the heating capacity of the rotational speed N2 of the heating compressor 320, the minimum rotation The number was set to N2. For example, when operating at rotational speed N1, in order to supplement a heating capability, it is estimated that the ON time of the heater 324 increases and heating efficiency falls.

Then, by maintaining the heating compressor 320 at the minimum rotational speed N2 in the section after the time t7, the room temperature gradually decreases, and when the blowing air temperature falls below the Tq at the time t9, the heater 324 is finely turned on / off again. At the same time it is turned off, the blowing air temperature is adjusted to be approximately constant at Tq. As a result, subtle capacity adjustment of the heater 324 is performed while maintaining the heating compressor 320 at the minimum rotational speed N2, whereby the condensation temperature of the switching chamber condenser 321, the blowing air temperature, and the hot / cold switching chamber ( The entire room temperature of 301 is stabilized. In this way, as long as the load of the hot / cold switching room 301 does not fluctuate greatly, this state will be maintained.

In this way, when the blowing air temperature exceeds Tq, the heater 324 is finely turned on and off, and the blowing air temperature is adjusted to be approximately constant at Tq, thereby heating the heat pump system and the hot / cold switching room ( The difference in load of 301 can be compensated with precision. As a result, the condensation temperature of the switching room condenser 321, the blowing air temperature, and the whole room temperature of the hot / cold switching room 301 become stable, and the temperature of goods, such as a can drink, can be maintained with high precision.

In addition, the load of the hot / cold switching chamber 301 is estimated from the ambient temperature and the temperature setting of the second cold exclusive chamber 303, and the minimum rotational speed is compared with the heating capacity of each rotational speed of the heating compressor 320. By applying the determining control, the difference between the heating capability of the heat pump system and the load of the hot / cold switching chamber 301 can be made very small. As a result, the fall of the room temperature of the hot / cold switching room 301 can be suppressed, and the power consumption of the heater 324 can be reduced.

Further, if the condensation temperature exceeds the upper limit temperature Tq, control is performed to sequentially decelerate the heating compressor 320, thereby suppressing the switching chamber condenser 321 and its peripheral members from continuously exceeding the upper limit temperature Tq. As a result, the fluctuation of the room temperature accompanying the overheating of the switching room condenser 321 can be suppressed, and the temperature of goods, such as a can drink, can be maintained with high precision.

In addition, by designing the maximum heating capacity of the heat pump system to be equal to the heating capacity of the heater, while suppressing overheating of the switching chamber condenser 321 when the heating compressor 320 continuously operates at the highest rotational speed, The amount of change in the heating capacity due to the change in rotational speed becomes small, and the amount of power consumption of the heater 324 that compensates the difference between the heating capacity of the heat pump system and the load of the hot / cold switching room 301 can be suppressed.

In addition, by using a heat pump system that independently heats the hot / cold switching chamber 301 using the outside air as a heat source, the cooling load of the cold exclusive chamber 302 and the second cold exclusive chamber 303 is not changed. . For this reason, since a heating capability is stabilized, the smooth change of the room temperature of the hot / cold switching room 301 can be implement | achieved.

In addition, a time interval for sequentially increasing or decreasing the heating compressor 320 sequentially, that is, waiting time from changing the rotation speed of the heating compressor 320 to performing the next change is set to about several minutes to several ten minutes. It is preferable. Even if the rotation speed of the heating compressor 320 is rapidly increased or decelerated, the heating capacity cannot be changed rapidly. Therefore, if the rotation speed of the heating compressor 320 is changed rapidly after the room temperature is stabilized, the switching condenser 20 Its overheating increases, rather it increases fluctuations in room temperature.

Moreover, it is preferable to set also the shortest waiting time when the condensation temperature of the switching room condenser 321 exceeds the upper limit condensation temperature Tq and decelerates the heating compressor 320 about several minutes to several ten minutes. This causes the warming compressor 320 to be decelerated forcibly regardless of the room temperature. Therefore, if this waiting time is small, it is possible to reduce the durability of the warming compressor 320 by repeating the increase and decrease frequently.

In addition, in Embodiment 4, the heater 324 turns ON when the blowing air temperature detected by the blowing air temperature sensor 330 becomes lower than the upper limit temperature Tq of the condensation temperature, and is higher than the upper limit temperature Tq of the condensing temperature. When higher, it was controlled to be OFF. However, what is necessary is just to set the reference temperature which turns ON / OFF the heater 324 in the vicinity of the blowing air temperature required in order to maintain the temperature of goods, such as a canned drink, at target temperature. In addition, a slight difference may be provided between the ON temperature and the OFF temperature, and the control period may be adjusted to be longer in a range where the temperature of products such as canned drinks does not change. In addition, the same effect is obtained even when the heater 324 is turned ON / OFF using the ambient temperature of the heater 324 having a high correlation with the blowing air temperature, instead of the blowing air temperature detected by the blowing air temperature sensor 330. Lose.

As described above, the heat pump system of the vending machine according to the present invention includes a heater having a heating capacity equivalent to or higher than that of the heat pump system, and by adjusting the heating capacity of the heat pump system so as not to significantly exceed the load at the time of stability. It is possible to suppress fluctuations in the room temperature accompanying excessive temperature rise of the condensation temperature. Therefore, the present invention can also be applied to applications that require saving of small-capacity heating energy, such as a show case for simultaneously storing hot and cold drinks and a cup vending machine for a small amount of hot water supply.

Next, in the above conventional configuration, since the compressor and the heat source side heat exchanger are simultaneously cooled or heat-exchanged with a heat radiating fan, the air reaches the compressor even during the warming operation, and the warming capacity is reduced by the amount of heat radiated from the compressor, resulting in a decrease in efficiency. .

In addition, it is difficult to surround a cylindrical compressor such as a reciprocal compressor, which is not cylindrical, in close contact with a heat insulating material.

In addition, when a conventional air source side heat exchanger is used to prevent the air from reaching the compressor, and the conventional heat source side heat exchanger is used, the air flow opening area is small, so that the air volume decreases, so that the relative humidity of the air passage outlet air increases, so that the vicinity of the heat exchanger or the air outlet exit is increased. This can cause problems such as condensation.

Embodiments 5 to 7 of the present invention solve the above-described conventional problems, while suppressing heat dissipation from a compressor and increasing heating efficiency while ensuring a sufficient air volume for the heat source side heat exchanger in a narrow machine room of a vending machine. Offers a vending machine.

In order to solve the said conventional subject, the vending machine of this invention comprises the independent air path in the space area of the left-right direction of a compressor, and arrange | positions the outdoor heat exchanger and a heat dissipation fan formed by the helical fin tube inside the air path. The compressor is surrounded by a heat insulating material foamed and molded in accordance with the shape of the upper surface of the compressor.

Accordingly, by using a spiral fin tube heat exchanger which does not wind against the compressor and has a small air flow resistance, a sufficient amount of air can be secured even if the air passage cross section is small.

In addition, a moldable heat insulating material such as a polypropylene foam can be molded in accordance with the shape of the upper surface of the compressor, and the heat dissipation of the compressor can be suppressed while surrounding the compressor and suppressing an increase in the external dimensions.

The vending machine of this invention can suppress heat dissipation from a compressor, and can improve a heating capability. As a result, it is possible to further reduce the amount of power consumed when heated using a heat pump.

According to the present invention, the heat dissipation fan air-cools only the outdoor heat exchanger in the air passage, and the wind does not reach the compressor, so that the heat dissipation from the compressor can be suppressed and the warming ability can be improved. In addition, by using an outdoor heat exchanger formed of a helical fin tube, condensation can be prevented even if the cross section of the air passage is small, and the space in the left and right directions of the compressor can be effectively used in a narrow machine room, and in particular, a wide vending machine Effective in

In addition, even if the refrigerant leaks around the compressor, the present invention can be discharged from the slit to the outside of the machine room to prevent the leakage refrigerant from being filled inside the machine room.

Moreover, this invention can suppress heat dissipation of a compressor, suppressing increase of an external dimension.

Moreover, even if HC refrigerant leaks from the joint part of a compressor and piping, since a joint part is exposed to the vicinity of the air path opening part of an upper part of a compressor, it can be discharged to the outside of a machine room by a heat radiating fan.

In addition, the present invention can prevent the dew condensate out of the machine room.

EMBODIMENT OF THE INVENTION Hereinafter, although embodiment 5-6 of this invention are demonstrated referring drawings, the same code | symbol is attached | subjected about the structure similar to a prior art example or embodiment mentioned above, and the detailed description is abbreviate | omitted. In addition, this invention is not limited by this embodiment.

(Embodiment 5)

Fig. 15 is a refrigeration cycle diagram of the vending machine in Embodiment 5 of the present invention. Fig. 16 is a longitudinal cross-sectional view of the vending machine in Embodiment 5 of the present invention. 17A is a plan view of the machine room of the vending machine in Embodiment 5 of the present invention, and FIG. 17B is a cross-sectional view of the machine room of the vending machine in Embodiment 5 of the present invention. In addition, about the same structure operation | movement as before, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

As shown in FIG. 15, the vault of the vending machine is divided into three, cooling exclusive storage (hereinafter referred to as left chamber), cooling warming chamber B (hereinafter referred to as solid), and cooling warming chamber C (hereinafter referred to as the lower compartment). The use side unit 401A (specific use side unit), the use side unit 401B, and the use side unit 401C which are mentioned later are respectively provided, and each unit is provided with the blower, respectively. . The heat source side unit 402 and the blower 420 are formed in the vault outer side of the vending machine. And the cooling-heating apparatus of a vending machine is comprised by these heat source side units 402 and utilization side units 401A-401C.

In FIG. 16, the vending machine main body 430 is constituted by a hot / cold switching room 431 and a machine room 432. An indoor heat exchanger 433, an indoor fan 434, and a heater 435 are provided inside the hot / cold switching room 431. Inside the machine room 432, a compressor 418, an outdoor heat exchanger 419, and a heat radiating fan 420 are provided. The heat insulating material 456 is provided to surround the compressor 418.

As shown in FIG. 17A and FIG. 17B, the air path 436 independent of the compressor 418 is comprised, and the outdoor heat exchanger 419 and the heat radiating fan 420 are arrange | positioned inside the air path 436. As shown to FIG.                     

The operation and action of the vending machine configured as described above will be described below.

The case where the left chamber and the solid chamber are cooled and the right chamber is heated will be described. The switching valve 405A of the heat source side heat exchanger 419 opens, the switching valve 405B closes, and the switching valve 410A of the utilization side heat exchanger 412B to be cooled closes, and the switching valve 410B Is opened, the switching valve 411A of the use-side heat exchanger 412C to be heated is opened, and the switching valve 411B is closed.

As a result, a part of the refrigerant discharged from the compressor 418 passes through the refrigerant discharge pipe 403 and the switching valve 405A sequentially, and flows to the heat source side heat exchanger 419, while the remaining refrigerant passes the high pressure gas pipe 407. Through the switching valve 411A of the use side unit 401C to be heated, it flows into the use side heat exchanger 412C. The condensation liquid is then liquefied by the use side heat exchanger 412C and the heat source side heat exchanger 419. The refrigerant condensed and liquefied by these heat exchangers 412C and 419 is depressurized by the refrigerant flow rate control valves 414 and 415 of the use-side units 401A and 401B via the liquid pipe 409, and then the respective indoor heat exchangers ( 412A, 412B) to evaporate and vaporize.

The refrigerant passing through the utilization side heat exchanger 412A flows into the low pressure gas pipe 408, and the refrigerant passing through the utilization side heat exchanger 412B passes through the switching valve 410B and flows into the low pressure gas pipe 408. The refrigerant suction tube 404 and the gas-liquid separator 421 are sequentially sucked into the compressor 418. In this way, since the use-side indoor heat exchanger 412C acts as a condenser, the right chamber is warmed, and the left chamber and the solid chamber are cooled in the use-side heat exchangers 412A and 412B serving as the evaporator.

In addition, the indoor fan 434 is for circulating and heating the heat of the indoor heat exchanger 433 in the hot / cold switching room 431, and the heater 435 has a low heating capacity of the refrigerating cycle. It is energized at the start of low outside temperature.

The heat radiating fan 420 allows wind to flow in the air path 436, and allows heat exchange between the outdoor heat exchanger 419 and the air. Since the heat dissipation fan 420 and the outdoor heat exchanger 419 are accommodated in the air passage 436, the wind by the heat dissipation fan 420 flows in the air passage 436, and the compressor 418 disposed outside the air passage 436. The heat dissipation from the compressor 418 can be suppressed without air cooling. As a result, if the condensation temperature of the indoor heat exchanger 433 rises and the load is the same, the operation rate of the compressor 418 can be reduced, the amount of power consumption can be reduced, and energy saving can be achieved.

At this time, in the prior art, since the air path 436 is not constituted, the wind by the heat radiating fan 420 heats the heat between the outdoor heat exchanger and the air, and simultaneously cools the compressor 418. Heat dissipation is accelerated, condensation temperature of the indoor heat exchanger 433 falls, and heating efficiency falls.

16, 17A, and 17B, two heat dissipation fans 420 are arranged. In consideration of suitability of the capacity of the outdoor heat exchanger 419 and the air volume of the heat dissipation fan 420, one or more heat dissipation fans 420 are provided. It is good also as three or more.

In addition, the heat dissipation of the compressor 418 can be suppressed by surrounding the compressor 418 with the heat insulating material 437 foamed and molded in accordance with the shape of the compressor upper surface. As the heat insulating material 437, a polypropylene foam having high heat insulation and small heat deformation (for example, EPP-15P made of JSP) is preferable. In the foamed styrol which is another heat insulating material, a problem of heat deformation in an atmosphere of 70 ° C or higher occurs. In addition, in urethane, although heat resistance becomes high, since the problem of having hygroscopicity arises, it is not preferable.

As mentioned above, in this embodiment, the air path 436 independent of the horizontal direction of the compressor 418 is comprised, and the outdoor heat exchanger 419 and the heat radiating fan 420 are arrange | positioned inside the air path 436, The compressor 418 is not air-cooled by the wind by the heat radiating fan 420, and the heat dissipation from the compressor 418 is suppressed at the time of heating the heat pump, thereby increasing the condensation temperature of the indoor heat exchanger 433. As a result, when the load is the same, the operation rate of the compressor 418 can be reduced, the amount of power consumption is reduced, and energy saving is achieved.

In addition, in this embodiment, since the heat insulating material 437 which surrounds the compressor 418 is foam-molded with polypropylene, heat insulation is high, heat deformation becomes small, and the heat radiation of the compressor 418 is suppressed while suppressing increase of an external dimension. Can be suppressed.

Moreover, the material of the heat insulating material 437 may be made into foam rubber, and it has the characteristics that heat insulation is high and thermal deformation is small like a polypropylene material.

(Embodiment 6)

18 is a refrigeration cycle diagram of the vending machine according to Embodiment 6 of the present invention. 19 is an overall longitudinal cross-sectional view of the vending machine in Embodiment 6 of the present invention. 20 is a sectional view of a machine room of the vending machine according to Embodiment 6 of the present invention. 21 is a perspective view of an outdoor heat exchanger according to Embodiment 6 of the present invention.

As shown in FIG. 18, the vending machine of the present invention includes a storage chamber including a hot / cold switching chamber 431, a cold dedicated chamber 438, and a second cold dedicated chamber 439, and R600a as a refrigerant. Thus, a high temperature receiver type compressor 450, an indoor condenser 451 installed in the hot / cold switching chamber 431, an outdoor heat exchanger 452 installed outside the storage chamber and acting as an evaporator, and an expansion valve 453 are included. And a heating system dedicated to heating the hot / cold switching room 431.

As shown in FIG. 19 and FIG. 20, the compressor 446 is disposed in the machine room 432 of the vending machine 430. An independent air passage 450 is formed above the compressor 446, and an outdoor heat exchanger 448 and a heat radiating fan 420 are installed in the air passage 450. The slit 451 is provided in the lower surface side of the air path 450, and the heat insulating material 452 is provided so that the compressor 446 may be enclosed. In addition, the condensation sensor 453 for detecting the presence of condensation is attached to the pipe of the outdoor heat exchanger 448 by installing at the place where the evaporation temperature becomes. And the water supply sheet 452 which absorbs condensation water is stored in the compressor 446 side of the slit 451 formed in the air path 450, and the water condensation water of the air path constitution member 455 which comprises the air path 450. It is provided in the part 456.

As shown in FIG. 21, the spiral heat exchanger tube 459 which spirally wound the fin 458 in the tube 457 is used for the outdoor heat exchanger 448. As shown in FIG.

The operation and action of the vending machine configured as described above will be described below.

First, when cooling the hot / cold switching room 431, after the high temperature compressor 446 is stopped, the compressor 418 is driven. The refrigerant discharged from the compressor 418 is condensed in the outdoor heat exchanger 419 acting as a condenser, and then depressurized by the expansion valve A443, the expansion valve B444, and the expansion valve C445, respectively, and the indoor evaporator ( 440, an evaporator 441, and a second evaporator 442. The refrigerant evaporated by the indoor evaporator 440, the evaporator 441, and the second evaporator 442 is returned to the compressor 418.

At this time, the storage chamber having reached a predetermined temperature in the hot / cold switching chamber 431, the cold dedicated chamber 438, and the second cold dedicated chamber 439 includes a corresponding expansion valve A443, expansion valve B444, The expansion valve C445 is closed to stop the supply of the refrigerant. In addition, the compressor 418 stops operation when all the storage chambers reach the predetermined temperature.

Next, when the hot / cold switching chamber 431 is warmed up, the compressor 418 is operated while the expansion valve A443 is closed to cool the cold exclusive chamber 438 and the second cold exclusive chamber 439. At the same time, the high temperature compressor 446 is driven. The refrigerant discharged from the high temperature compressor 446 is condensed in the indoor condenser 447, and then depressurized by the expansion valve 449 and supplied to the outdoor heat exchanger 448. The refrigerant evaporated in the outdoor heat exchanger 448 is refluxed to the high temperature compressor 446.

Thus, in order to have a dedicated heating system for warming the hot / cold switching room 431, by optimizing the matching of the dedicated outdoor heat exchanger 448 and the high temperature receiver compressor 446, the compressor 446 Ensure durability and high efficiency.

Further, in arranging the outdoor heat exchanger 448 in the upper space of the compressor 446, by using the heat exchanger 459 formed of a helical fin tube, the outdoor heat exchanger 448 is compact in a planar state. do. Moreover, since the space | interval between the fins 458 of the helical fin tube heat exchanger 459 is large, and it is connected in a spiral form, sufficient wind volume can be ensured even if the wind resistance becomes small and the air passage cross section is small, Condensation can be prevented from occurring near the heat exchanger or the outlet of the furnace. In addition, dust is not deposited, and generation of lattice blockage between the pins 458 can be suppressed.

The heat radiating fan 420 allows wind to flow in the air path 450, and allows heat exchange between the outdoor heat exchanger 448 and the air. Since the heat dissipation fan 420 and the outdoor heat exchanger 448 are accommodated in the air passage 450, wind by the heat dissipation fan 420 flows in the air passage 450, and the compressor 446 disposed outside the air passage 450. The heat dissipation from the compressor 446 can be suppressed without air cooling.

Since the slit 451 is formed in the lower surface side of the air path 450, the total area of the inlet of the air path 450 becomes large, and the amount of suction air into the air path 450 by the heat radiating fan 420 increases, and the outdoor heat exchange is performed. The heat exchange ability with the group 448 increases.

In addition, when condensation is detected by the condensation sensor 453, the heating system stops the operation.

In addition, the water supply sheet 454 is provided in the compressor 446 side of the slit 451 provided in the air passage 450 and the condensation water storage part 456 of the air passage structural member 455 constituting the air passage 450. The water supply sheet 454 absorbs the condensation water discharged while detecting the occurrence of condensation and stopping the operation. The water supply sheet 454 containing this water evaporates water by the heat from the compressor 446 and the continuous operation of the heat radiating fan 420.

In addition, in the heating single heat pump, when the water supply sheet 454 is not provided, the dew condensation water is guided to the outdoor heat exchanger 419 on the cooling side or the compressor 418, and to the arrangement on the cooling side. You may evaporate by this and in this case, the efficiency of a cooling side will improve.                     

As described above, in the present embodiment, the heat exchanger 459 and the heat dissipation fan 420 that form an independent air passage 450 on the upper side of the compressor 446 and are formed of spiral fin tubes inside the air passage 450. Place it. Therefore, in the structure, the heat exchanger 459 becomes compact in a planar state, and the space above the compressor 446 in the narrow machine room 432 can be utilized effectively. In addition, even if the wind resistance is small and the air passage cross section is small, a sufficient air volume can be ensured, and condensation can be prevented from occurring near the outlet of the outdoor heat exchanger 448 or the air passage 450. In addition, lattice clogging due to dust does not occur, and management is not necessary.

The compressor 446 is preferably a pole concentrated winding DC inverter compressor. Unlike the conventional method of inserting a pre-wound motor coil into the slot, as in the conventional distributed damping compressor, since the motor coil is directly wound into the slot, the winding pitch is very narrow and the coil end dimension of the motor is reduced. It can be reduced to about one third, and the height dimension of the compressor can be kept low. Therefore, it becomes easy to ensure the space above the compressor 446.

If there is room in the upper space of the compressor 446, the spiral fin tube heat exchanger 459 constituting the outdoor heat exchanger 448 provided in the space may be a two-stage configuration. In this case, the evaporation ability can be improved.

Moreover, in this embodiment, since the slit 451 is formed in the lower surface side of the air path 450, the total area of the inlet of the air path 450 becomes large, and the heat exchange ability with the outdoor heat exchanger 448 increases.                     

In addition, in this embodiment, the dew condensation sensor 453 which detects the presence or absence of condensation is provided in the lower side piping of the outdoor heat exchanger 448, and it is installed in the place which becomes evaporation temperature, and the dew condensation sensor which detects the presence of condensation. When condensation is detected by 453, the operation of the heating system is stopped to prevent the condensation water from flowing out of the machine room 432.

In the present embodiment, the water supply sheet 454 is formed on the compressor 446 side and the condensation water storage part 456 of the slit 451 formed in the air passage 450, and the operation is stopped by detecting the occurrence of condensation. The condensation water discharged | emitted until before is absorbed by the water supply sheet 454. In this way, the dew condensation water can be prevented from flowing out of the machine room 432.

(Seventh Embodiment)

It is sectional drawing of the machine room of the vending machine in Embodiment 7 of this invention. In addition, about the structure action similar to Embodiment 6, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

22, the compressor 446 is equipped with the discharge pipe 460 and the suction pipe 461, and the heat insulating material surrounding the compressor 445 by the joint part of the discharge pipe 460 and the suction pipe 461 ( 462 is exposed outside.

The operation and action of the vending machine configured as described above will be described below.

First, the joints of the pipes of the discharge pipe 460 and the suction pipe 461 are exposed from the heat insulating material 462. Therefore, even when HC refrigerant leaks from the joints of the pipes of the discharge pipe 460 and the suction pipe 461 when the HC coolant is used, the heat radiating fan 420 is provided at the air passage opening (slit 451) in the upper portion of the compressor 446. ) Is discharged to the outside of the machine room 432. It is possible to prevent the leakage refrigerant from being filled inside the machine room 432, and the safety of the ignition source is further improved.

As described above, the vending machine according to the present invention can maintain the temperature of the compressor at a high temperature at the time of heating the heat pump and improve the heating capability, and thus can be applied to applications such as cold storage.

Claims (24)

A storage compartment for cooling, a warmable storage compartment insulated from the storage compartment for cooling, a cooling system for cooling the storage compartment for cooling, and a heating installed independently of the cooling system to warm the warmable storage compartment. And a cooling system connects a compressor, an outdoor heat exchanger, and an evaporator provided in the storage chamber exclusively for cooling, and the heating system automatically connects a compressor, a condenser installed in the warmable storage chamber, and an evaporator installed outdoors. As a vending machine, When the warmable storage compartment is heated, it is installed in a warmable storage compartment while maintaining a commercial evaporation temperature of the evaporator installed outdoors at -10 to 10 ° C. by exchanging heat with outdoor air with the evaporator installed outdoors. And a commercial condensation temperature of the condenser at 60 to 80 ° C. to warm the inside of the warmable storage chamber to 50 to 70 ° C., and to set the refrigerant of the heating system to R600a and to operate the compressor with an inverter. The method according to claim 1, further comprising an evaporator of the cooling system in the warmable storage chamber, the hot / cold switching chamber to cool the inside of the hot / cold switching chamber by the evaporator during the cooling of the hot / cold switching chamber , vending machine. The vending machine according to claim 1 or 2, wherein the inverter-driven compressor of the heating system is a receiver-type compressor in which the shell is maintained at an evaporation pressure. The vending machine according to claim 1 or 2, wherein the inverter-driven compressor of the heating system is controlled at a minimum rotational speed at which no intermittent operation occurs even at an outside temperature of 15 ° C. The compressor of the inverter drive of a heating system is the rotation speed which is higher than normal rotation speed at the time of pull-up, and is not intermittent operation at the time of pull-up, and is lower than the normal rotation speed at the time of stability, and is not interrupted operation. RPM controlled, vending machine. With the hot / cold change room which holds a product, A heat pump system comprising a compressor, a condenser, an expansion mechanism, and an evaporator, and heating the hot / cold switching chamber by using atmospheric heat; A heater as a heating source for heating the hot / cold switching room simultaneously with the heat pump system; An indoor temperature sensor detecting an indoor air temperature of the hot / cold switching room; And a temperature adjusting control device for controlling the rotation speed of the compressor according to the comparison of the detected temperature of the room temperature sensor with a preset reference temperature. The heating capacity of the heat pump system is equal to or less than the heating capacity of the heater, When the detected temperature of the room temperature sensor is equal to or lower than the shift UP temperature at which the rotation speed of the compressor is increased, the compressor is increased at every shift UP waiting time, And the compressor decelerates every shift down time when the detected temperature of the room temperature sensor is equal to or higher than the shift down temperature. The method of claim 6, further comprising a condensation temperature sensor for detecting the temperature of the condenser, And a rotation speed of the compressor is decelerated when a detected temperature of the condensation temperature sensor exceeds a predetermined value after a predetermined time after changing the rotation speed of the compressor. The outdoor air temperature sensor according to claim 6, which detects the outside air temperature; A driving mode storage device for storing a temperature setting state of a product storage room adjacent to the hot / cold switching room; Characterized in that the heating load of the hot / cold switching room is estimated from the detected temperature of the ambient temperature sensor and the temperature setting state of the operation mode memory device, and the minimum rotational speed of the compressor is determined according to the magnitude of the heating load. vending machine. The outdoor air temperature sensor according to claim 7, which detects an outside air temperature; A driving mode storage device for storing a temperature setting state of a product storage room adjacent to the hot / cold switching room; Characterized in that the heating load of the hot / cold switching room is estimated from the detected temperature of the ambient temperature sensor and the temperature setting state of the operation mode memory device, and the minimum rotational speed of the compressor is determined according to the magnitude of the heating load. vending machine. The heater according to any one of claims 6 to 9, further comprising: a heater located below the wind of the condenser; A blowing air temperature sensor detecting a blowing air temperature of an overheat source consisting of the condenser and the heater or an ambient temperature of the heater; Further comprising a control device for adjusting the capacity to control the heater in accordance with the comparison of the detected temperature of the blowing air temperature sensor and a preset reference temperature, The ability adjustment heater ON temperature used as a reference which turns on a said heater, and the ability adjustment heater OFF temperature used as a reference which turns off said heater are set, and it is controlled so that the detection temperature of the said blowing air temperature sensor may become constant. vending machine. delete delete delete delete delete delete delete delete delete delete delete delete delete delete

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