JP2007219905A - Automatic vending machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce power consumption by preventing deterioration in the efficiency of a compressor during the warning operation of a cooling/warming cycle. <P>SOLUTION: This automatic vending machine is provided with a compressor 120 for cooling installed in a cooling cycle 125 and a compressor 106 for cooling/warming installed in a cooling/warming cycle 115, and the compressor 106 for cooling/warming is configured so that the highest number of revolutions in warming is set to be lower than the highest number of revolutions in cooling. Thus, it is possible to achieve cooling/warming by a single compressor, and to improve the reliability of the compressor for cooling/warming, and to sharply reduce the power consumption of the automatic vending machine. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a vending machine that warms or cools a product such as a can beverage and sells it by using latent heat generated when the refrigerant compressed by the compressor condenses, and can be heated. The present invention relates to a vending machine equipped with a device.

  In recent years, demands for reducing power consumption for vending machines have increased, and as a means for reducing power consumption, one utilizing waste heat generated by cooling has been proposed (for example, see Patent Document 1).

  Hereinafter, a conventional vending machine will be described with reference to the drawings.

  FIG. 10 is a refrigerant circuit diagram of a conventional vending machine.

  As shown in FIG. 10, the conventional vending machine includes a storage room 4 including a cooling / heating switching chamber 1, a cooling-only room 2, and a second cooling-only room 3, and is installed in the cooling / heating switching room 1. The indoor heat exchanger 5, the evaporator 6 installed in the cooling chamber 2, the second evaporator 7 installed in the second cooling chamber 3, and the outside installed outside the storage chamber 4 It has a cooling and heating cycle 10 composed of a heat exchanger 8 and a compressor 9.

  The expansion valve A11, the expansion valve B12, and the expansion valve C13 each have a closing function while reducing the pressure of the refrigerant passing therethrough. The on-off valve A14, the on-off valve B15, the on-off valve C16, and the on-off valve D17 are respectively It controls the presence or absence of refrigerant flow.

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

  When cooling the cooling / warming switching chamber 1, the on-off valve A14 and the on-off valve D17 are opened, the on-off valve B15 and the on-off valve C16 are closed, and the compressor 9 is driven. The refrigerant discharged from the compressor 9 is condensed in the outdoor heat exchanger 8, and then decompressed by the expansion valve A11, the expansion valve B12, and the expansion valve C13, respectively, and the indoor heat exchanger 5, the evaporator 6, and the second To the evaporator 7. Then, the refrigerant evaporated in the indoor heat exchanger 5, the evaporator 6, and the second evaporator 7 is returned to the compressor 9.

  At this time, the storage chamber 4 that has reached a predetermined temperature among the cooling / heating switching chamber 1, the cooling dedicated chamber 2, and the second cooling dedicated chamber 3 closes the expansion valve A11, the expansion valve B12, and the expansion valve C13. Then, supply of the refrigerant is stopped. Further, when all the storage chambers 4 reach a predetermined temperature, the operation of the compressor 9 is stopped.

  Next, when heating the cooling / warming switching chamber 1, the on-off valve A14, the on-off valve D17, and the expansion valve A11 are closed, the on-off valve B15 and the on-off valve C16 are opened, and the compressor 9 is driven. The refrigerant discharged from the compressor 9 is partially condensed in the indoor heat exchanger 5 and again condensed in the outdoor heat exchanger 8, and then decompressed by the expansion valve B12 and the expansion valve C13, respectively. , And supplied to the second evaporator 7. Then, the refrigerant evaporated in the evaporator 6 and the second evaporator 7 returns to the compressor 9.

  In addition, the storage chamber 4 that has reached a predetermined temperature among the cooling-only chamber 2 and the second cooling-only chamber 3 closes the expansion valve B12 and the expansion valve C13 to stop the supply of the refrigerant. Further, when all the storage chambers 4 reach a predetermined temperature, the operation of the compressor 9 is stopped.

Here, the cooling and heating switching chamber 1 can be efficiently heated by using the condensation waste heat of the refrigerant generated when the cooling only chamber 2 and the second cooling only chamber 3 are cooled. The amount of power consumption can be reduced as compared with the case where the cooling / heating switching chamber 1 is heated using another heating means.
Japanese Patent Laid-Open No. 5-233941

  However, in the conventional configuration, in the vending machine in which the temperature of the cooling beverage is about 5 ° C. and the temperature of the heating beverage is about 55 ° C., in order to realize the cooling / heating switching chamber with a single compressor, There has been a problem that it is necessary to newly develop a compressor that can be used under severe conditions such as an evaporation temperature of −40 ° C. to + 10 ° C. and a condensation temperature of 40 ° C. to 70 ° C.

  In addition to the above issues, the power consumption is so high that it is sufficiently reliable and can save energy in order to suppress global warming in recent years because it is installed in a cooling and heating cycle that is installed outdoors as a vending machine. The problem was that it was necessary to develop a compressor and refrigeration system with reduced noise.

Further, in order to realize a cooling and heating cycle in a single compressor using refrigerant such as R407C and R290 and CO ₂ is a low-boiling refrigerant is refrigerant which has been conventionally used, high pressure and compression during heating The internal temperature of the machine becomes extremely high, and the reliability of the compressor is ensured because the load resistance inside the compressor, the durability of the high-pressure piping is reduced, or the temperature of internal parts is likely to deteriorate. It was difficult. Such a problem of ensuring reliability becomes more conspicuous particularly when installed in a vending machine installed under a large fluctuation of the outside air temperature because it is installed outdoors. On the other hand, even when R134a generally used in refrigerators or the like is used as a high boiling point refrigerant, the pressure was about twice as high as that of R600a, and the internal temperature of the compressor was also high.

  The present invention solves the above-described conventional problems, and in order to realize cooling / heating with the same compressor, pays attention to the operating conditions of the compressor, improves reliability, and consumes power during heating. The purpose is to provide a compressor and a vending machine that can reduce energy consumption and realize energy saving.

  In order to solve the above-described conventional problems, a vending machine according to the present invention is provided with a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between a cooling operation and a heating operation, and the cooling cycle. A cooling compressor and a cooling / heating compressor provided in the cooling / heating cycle, the cooling / heating compressor having a sealed container and an electric compression element provided in the sealed container. In addition, an inverter compressor that is operated at a plurality of rotational speeds, R600a is enclosed as a refrigerant in the cooling and heating cycle, and the maximum operating rotational speed when the cooling and heating cycle is in the heating operation is the cooling operation. It is lower than the maximum operating speed of

  As a result, even when cooling / heating is realized with a single compressor, the load resistance inside the compressor and the durability of the high-pressure piping can be secured by using R600a having a very high high-pressure pressure. The temperature rise inside the compressor can also be suppressed.

  In addition, the maximum operating speed of the inverter compressor is reduced during the cooling operation during the heating operation, which is a severe condition in terms of the reliability of the compressor because the highest pressure is the highest among the operating conditions of the cooling / heating cycle. By making it lower than the maximum operation speed, it becomes possible to further improve the reliability during the heating operation.

  In addition, it is possible to achieve a heating efficiency that is twice as high as that of a heating means such as an electric heater that has a heating efficiency of about 1. Further, the inverter is driven in both the cooling operation and the heating operation. By operating the compressor with a high load, the compressor can be operated at a high rotation speed to increase the refrigeration capacity, and at a low load, it can be continuously operated at a low rotation speed to greatly reduce power consumption. Is possible.

  The vending machine of the present invention includes a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between the cooling operation and the heating operation, a cooling compressor provided in the cooling cycle, A cooling / heating compressor provided in the cooling / heating cycle, and R600a is sealed as a refrigerant in the cooling / heating cycle, and the cooling / heating compressor is provided in a sealed container and the sealed container. And an electric compressor element that is operated at a plurality of rotational speeds, wherein the thickness of the suction lead provided in the electric compression element is set to the thickness of the suction lead of the cooling compressor. Thus, the thickness is increased to 1.2 to 2.0.

  As a result, in comparison with the cooling compressor, especially in the cooling compressor where the refrigerant circulation amount increases during the heating operation, paying attention to the technical problem that the load of the suction lead, which has a large influence of the refrigerant circulation amount, becomes large, the suction By improving the reliability of the lead by improving the rigidity of the reed, it is possible to prevent the intake lead opening from becoming excessive even during heating, where the refrigerant circulation rate increases compared to during cooling. Therefore, it is possible to provide a vending machine with improved reliability.

  The vending machine of the present invention includes a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between the cooling operation and the heating operation, a cooling compressor provided in the cooling cycle, A cooling / heating compressor provided in the cooling / heating cycle, and R600a is sealed as a refrigerant in the cooling / heating cycle, and the cooling / heating compressor is provided in a sealed container and the sealed container. And an electric compressor element operated at a plurality of rotational speeds, wherein the spring constant of the suction lead provided in the electric compressor element is set to the spring constant of the suction lead of the cooling compressor. Thus, the ratio is increased to 1.5 or more and 3.0 or less.

  As a result, compared to the cooling compressor, particularly in a cooling compressor where the refrigerant circulation amount increases during the heating operation, the discharge lead due to the impact force when the discharge lead collides with other parts due to the influence of the refrigerant circulation amount. Focusing on technical issues that increase the load on the discharge lead, by improving the impact resistance strength of the discharge lead during heating, when the refrigerant circulation rate increases compared to during cooling, improving the reliability of the discharge lead Since the reliability of the cool / warm compressor can be improved, a vending machine with improved reliability can be provided.

  The vending machine of the present invention includes a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between the cooling operation and the heating operation, a cooling compressor provided in the cooling cycle, A cooling / heating compressor provided in the cooling / heating cycle, and R600a is sealed as a refrigerant in the cooling / heating cycle, and the cooling / heating compressor is provided in a sealed container and the sealed container. And an electric compressor element that is operated at a plurality of rotation speeds, and the impact fatigue strength of the discharge lead provided in the electric compression element is determined according to the shock resistance of the discharge lead of the cooling compressor. The fatigue strength is increased so that the ratio is 1.2 or more.

  As a result, compared to the cooling compressor, particularly in a cooling compressor where the refrigerant circulation amount increases during the heating operation, the discharge lead due to the impact force when the discharge lead collides with other parts due to the influence of the refrigerant circulation amount. Focusing on technical issues that increase the load on the discharge lead, by improving the impact resistance strength of the discharge lead during heating, when the refrigerant circulation rate increases compared to during cooling, improving the reliability of the discharge lead Since the reliability of the cool / warm compressor can be improved, a vending machine with improved reliability can be provided.

  The vending machine of the present invention can improve the reliability of the cooling / cooling compressor while realizing cooling / heating with a single compressor, and greatly reduce the power consumption of the vending machine. be able to.

  The invention according to claim 1 includes a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between the cooling operation and the heating operation, a cooling compressor provided in the cooling cycle, and the cooling A cooling / heating compressor provided in the heating cycle, the cooling / heating compressor having a sealed container and an electric compression element provided in the sealed container and operated at a plurality of rotation speeds. In the inverter compressor, R600a is enclosed as a refrigerant in the cooling and heating cycle, and the cooling and heating cycle is such that the maximum operating speed during the heating operation is lower than the maximum operating speed during the cooling operation. is there.

  As a result, even when cooling / heating is realized with a single compressor, the load resistance inside the compressor and the durability of the high-pressure piping can be secured by using R600a having a very high high-pressure pressure. The temperature rise inside the compressor can also be suppressed.

  In addition, the maximum operating speed of the inverter compressor is reduced during the cooling operation during the heating operation, which is a severe condition in terms of the reliability of the compressor because the highest pressure is the highest among the operating conditions of the cooling / heating cycle. By making it lower than the maximum operation speed, it becomes possible to further improve the reliability during the heating operation.

  In addition, it is possible to achieve a heating efficiency that is twice as high as that of a heating means such as an electric heater that has a heating efficiency of about 1. Further, the inverter is driven in both the cooling operation and the heating operation. By operating the compressor with a high load, the compressor can be operated at a high rotation speed to increase the refrigeration capacity, and at a low load, it can be continuously operated at a low rotation speed to greatly reduce power consumption. Is possible.

  According to a second aspect of the present invention, in the first aspect of the present invention, the refrigerant circulation amount at the maximum operation speed during the heating operation approximates the refrigerant circulation amount at the maximum operation speed during the cooling operation. The maximum operation speed during the heating operation is lower than the maximum operation speed during the cooling operation.

  This increases the amount of refrigerant circulating in the heating operation with a high evaporation temperature, increases the stress applied to the valve provided in the electric compression element, increases the opening / closing distance of the valve, and increases the burden on the valve. In order to compress the refrigerant, it is possible to avoid a severe sliding condition such as a crankshaft or a bearing due to an increase in the load during compression, and to provide a highly reliable cooling and heating cycle.

  The invention according to claim 3 is the invention according to claim 1, to the extent that the stress or impact applied to the valve mechanism provided in the electric compression element of the cold compressor during the heating operation is relieved. The maximum operating rotational speed during the heating operation of the cooling / warming compressor is set lower than the maximum operating rotational speed during the cooling operation.

  As a result, the stress or impact applied to the suction and discharge leads, which are valve mechanisms provided in the electric compression element, is alleviated to the extent that durability and reliability can be ensured, and the reliability of the compressor for cooling and heating is improved. And a highly reliable cooling and heating cycle can be provided.

  According to a fourth aspect of the present invention, in the invention according to any one of the first to third aspects, the maximum operating rotational speed during the heating operation of the cooling compressor is changed to the maximum operating rotational speed during the cooling operation. On the other hand, the ratio is lowered to 0.5 or more and 0.9 or less.

  Thereby, in addition to the effect of the invention according to any one of claims 1 to 3, the reliability of the cooling / cooling compressor can be improved in a more stable range, and a highly reliable cooling / heating cycle can be achieved. Can be provided.

  The invention according to claim 5 is a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between a cooling operation and a heating operation, a cooling compressor provided in the cooling cycle, and the cooling A cooling compressor provided in the heating cycle, and R600a is enclosed as a refrigerant in the cooling heating cycle, and the cooling compressor is provided in a sealed container and in the sealed container. And an electric compressor element that is operated at a plurality of rotation speeds, and the thickness of the suction lead provided in the electric compression element is set to the thickness of the suction lead of the cooling compressor. The ratio is increased so that the ratio is 1.2 or more and 2.0 or less, and the stress resistance of the suction lead due to the increase in the amount of refrigerant circulation during the heating operation is increased.

  As a result, in comparison with the cooling compressor, especially in the cooling compressor where the refrigerant circulation amount increases in the heating operation, paying attention to the technical problem that the load of the suction lead having a large influence of the refrigerant circulation amount becomes large, By improving the reliability of the lead by improving the rigidity of the reed, it is possible to prevent the intake lead opening from becoming excessive even during heating, where the refrigerant circulation rate increases compared to during cooling. Therefore, it is possible to provide a vending machine with improved reliability.

  The invention according to claim 6 includes a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between the cooling operation and the heating operation, a cooling compressor provided in the cooling cycle, and the cooling A cooling compressor provided in the heating cycle, and R600a is enclosed as a refrigerant in the cooling heating cycle, and the cooling compressor is provided in a sealed container and in the sealed container. And an electric compressor element that is operated at a plurality of rotation speeds, and the spring constant of the suction lead provided in the electric compressor element is set to the spring constant of the suction lead of the cooling compressor. The ratio is increased to 1.5 or more and 3.0 or less to increase the stress resistance of the suction lead due to the increase in the refrigerant circulation amount during the heating operation.

  As a result, in comparison with the cooling compressor, especially in the cooling compressor where the refrigerant circulation amount increases during the heating operation, paying attention to the technical problem that the load of the suction lead, which has a large influence of the refrigerant circulation amount, becomes large, the suction By improving the reliability of the lead by improving the rigidity of the reed, it is possible to prevent the intake lead opening from becoming excessive even during heating, where the refrigerant circulation rate increases compared to during cooling. Therefore, it is possible to provide a vending machine with improved reliability.

  The invention according to claim 7 includes a cooling cycle for performing a cooling operation, a cooling / heating cycle capable of switching between the cooling operation and the heating operation, a cooling compressor provided in the cooling cycle, and the cooling A cooling compressor provided in the heating cycle, and R600a is enclosed as a refrigerant in the cooling heating cycle, and the cooling compressor is provided in a sealed container and in the sealed container. And an electric compressor element that is operated at a plurality of rotation speeds, and the impact fatigue strength of the discharge lead provided in the electric compression element is the impact fatigue resistance of the discharge lead of the cooling compressor. The strength is increased so that the ratio becomes 1.2 or more, and the impact resistance of the discharge lead due to the increase in the circulation amount of the refrigerant during the heating operation is increased.

  As a result, compared to the cooling compressor, particularly in a cooling compressor where the refrigerant circulation amount increases during the heating operation, the discharge lead due to the impact force when the discharge lead collides with other parts due to the influence of the refrigerant circulation amount. Focusing on technical issues that increase the load on the discharge lead, by improving the impact resistance strength of the discharge lead during heating, when the refrigerant circulation rate increases compared to during cooling, improving the reliability of the discharge lead Since the reliability of the cool / warm compressor can be improved, a vending machine with improved reliability can be provided.

  The invention according to claim 8 is the invention according to claim 7, wherein valve steel is used for the material of the discharge lead provided in the electric compression element of the cooling compressor, and the electric compression element of the cold temperature compressor is provided. Stainless steel valve steel is used as the material of the discharge lead.

  As a result, compared to the cooling compressor, particularly in a cooling compressor where the refrigerant circulation amount increases during the heating operation, the discharge lead due to the impact force when the discharge lead collides with other parts due to the influence of the refrigerant circulation amount. Focusing on technical issues that increase the load on the material, the impact resistance strength of the discharge lead during heating is increased when the refrigerant circulation rate is increased compared to during cooling, and the material aspect should be improved without major changes to the structure. In addition, since the reliability of the cooling / warming compressor can be improved by improving the reliability of the discharge lead, a vending machine with improved reliability can be provided.

  According to a ninth aspect of the present invention, in the invention according to any one of the first to fourth aspects, the electric motor of the cooling / warming compressor is operated at the maximum rotational speed during the cooling operation. By setting the motor torque so that it is at least larger than the torque in the state where the electric motor of the cooling compressor is operating at the maximum number of revolutions, the amount of refrigerant circulating during the heating operation of the cooling / heating compressor is increased. It is designed to withstand the load.

  As a result, compared with the cooling compressor, especially in the cooling / warming compressor in which the refrigerant circulation amount increases during the heating operation, even when the load of the electric motor increases with the increase in the refrigerant circulation amount, the load is higher. By providing an electric motor with increased torque at the time of cooling / cooling compressors, the reliability of the cooling / cooling compressors can be further improved, and thus a vending machine with improved reliability can be provided. .

  The invention according to claim 10 is the invention according to any one of claims 1 to 9, wherein the cooling compressor is installed on an air passage that performs forced cooling of the machine room by a machine room fan. The compressor for cooling / heating is installed at a place other than the air path.

  As a result, it is possible to prevent a reduction in the intake gas temperature of the cold compressor, particularly at a low outside air temperature at which the cold compressor performs the heating operation, so that the cycle efficiency of the cooling / heating cycle during the warming operation can be reduced. The power consumption of the vending machine can be reduced.

  The invention according to claim 11 is the invention according to any one of claims 1 to 10, wherein a cover for covering the airtight container is provided outside the airtight container of the compressor for cooling and heating. .

  As a result, it is possible to prevent a reduction in the intake gas temperature of the cold compressor, particularly at a low outside air temperature at which the cold compressor performs the heating operation, so that the cycle efficiency of the cooling / heating cycle during the warming operation can be reduced. The power consumption of the vending machine can be reduced.

  The invention according to claim 12 is the invention according to any one of claims 1 to 11, wherein R600a is enclosed as a refrigerant in the cooling cycle.

  As a result, it is possible to provide an environment-friendly vending machine that further contributes to the prevention of global warming, and there is also an advantage in terms of manufacturing and service that applies the same refrigerant as the cooling and heating cycle.

  In addition, since the vending machine is cooled and heated in a system separated into two independent circuits, a cooling cycle and a cooling and heating cycle, all refrigerant leaks even in the event of a leak of flammable refrigerant A certain safety factor can be expected for the explosion-proof safety of a vending machine suitable for a combustible refrigerant.

  A thirteenth aspect of the invention is the invention according to any one of the first to twelfth aspects of the invention, wherein the pressure in the sealed container of the cooling compressor and the cooling / warming compressor is a low pressure type.

  As a result, the amount of refrigerant dissolved in refrigerating machine oil can be reduced as compared with the case where the inside of the hermetic container is a high-pressure type. Since it can be suppressed, the absolute amount when a refrigerant leaks can be reduced, the amount of flammable refrigerant held in the system can be reduced, and explosion-proof safety can be improved.

  In addition, since the vending machine is cooled and heated in a system separated into two independent circuits, a cooling cycle and a cooling and heating cycle, all refrigerant leaks even in the event of a leak of flammable refrigerant A certain safety factor can be expected for the explosion-proof safety of a vending machine suitable for a combustible refrigerant.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected about the same structure as embodiment in the prior art example or previously demonstrated, and the detailed description is abbreviate | omitted. Further, the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a refrigerant circuit diagram of a vending machine according to Embodiment 1 of the present invention, FIG. 2 is a perspective view of a refrigeration apparatus constituting a refrigeration cycle in the same embodiment, and FIG. 3 is an automatic in the same embodiment. FIG. 4 is a plan sectional view of the cooling / cooling compressor and the cooling compressor as seen from above the vending machine, and FIG. 4 is a longitudinal sectional view of the cooling / heating compressor in the same embodiment.

  1 to 4, the vending machine of the present invention includes a storage chamber 104 including a cooling / heating switching chamber 101, a cooling-dedicated chamber 102, and a second cooling-dedicated chamber 103, and is installed in a cover 105. Compressor 106, indoor heat exchanger 108 installed in cooling / warming switching chamber 101, outdoor heat exchanger 110 installed outside storage chamber 104, four-way valve for switching the refrigerant flow path during cooling and heating 111, a cooling capillary tube 112 serving as an expansion mechanism, a heating capillary tube 113, and a dryer 114, and includes a cooling / heating cycle 115 that exclusively cools and heats the cooling / heating switching chamber 101, and performs cooling. Compressor 120, evaporator 121 installed in cooling chamber 102, second evaporator 122 installed in second cooling chamber 103, expansion valve 1 as an expansion mechanism 3, a second expansion valve 124, and a condenser 125 formed integrally with the cooling and heating cycle 115 side, and a cooling cycle 126 that exclusively cools the cooling dedicated chamber 102 and the second cooling dedicated chamber 103. It has.

  Here, the cooling and heating cycle 115 and the cooling cycle 126 are filled with R600a which is a hydrocarbon-based refrigerant having a low warming coefficient.

  The outdoor heat exchanger 110 and the condenser 125 are configured by a two-pass fin tube heat exchanger, and one of the passes is connected to the cooling and heating cycle 115, and the evaporator is used when the cooling and heating cycle 115 is heated. When cooling, it acts as a condenser, and the other path is connected to the cooling cycle 126.

  The indoor heat exchanger 108 and the outdoor heat exchanger 110 are an integrated heat exchanger 119 connected by two pipes, one of which includes a cooling capillary tube 112, a cooling check valve 127, and a dryer 114. The heating capillary tube 113 and the heating check valve 129 are connected in series on the other side.

  Here, the cooling check valve 127 is installed so that the refrigerant flows from the dryer 114 to the cooling capillary tube 112 in the forward direction and the refrigerant does not flow in the reverse direction from the cooling capillary tube 112 to the dryer 114. The The warming check valve 128 has a forward direction in which the refrigerant flows from the heating capillary tube 113 to the outdoor heat exchanger 110 and a reverse direction from the outdoor heat exchanger 110 toward the warming capillary tube 113. Installed so that refrigerant does not flow.

  In addition, a door 129 that opens and closes when a product is put into a vending machine is provided in front of the storage compartment 104 that is insulated.

  Next, the configuration of the cold / hot compressor 106 will be described.

  A mortar-shaped lower container 130 formed by deep drawing of a rolled steel plate and an inverted mortar-shaped upper container 131 are engaged, and the engagement portion is welded all around to form a sealed container 132. In the lower part of the hermetic container 132, mineral oil is stored as the refrigerating machine oil 134, and the electric compression element 140 is disposed. The electric compression element 140 is elastically supported on the bottom of the hermetic container 132 via a coil spring 142.

  The electric compression element 140 includes a stator 146 fixed below the block 144 and connected to an inverter drive circuit (not shown), and a rotor 150 containing a permanent magnet and fixed below the main shaft portion 148. An inverter-driven electric motor is formed, and the inverter drive circuit is always driven at an operation frequency different from that of the cooling compressor 120 operated at the commercial power supply frequency.

  The electric compression element 140 includes a block 144 that forms a cylinder 152, a piston 154 that is reciprocally inserted into a bore hole 153 of the cylinder 152, and a main shaft portion 148 that is pivotally supported by a bearing 156 of the block 144. A crankshaft 160 composed of a core shaft portion 158 and a connecting rod 162 connecting the eccentric shaft portion 158 and the piston 154 are provided, and the rotational motion of the crankshaft 160 is converted into the reciprocating motion of the piston 154.

  In addition, the space volume of the compression chamber 163 formed between the piston 154 and the bore hole 153 is changed by the reciprocating motion of the piston 154, so that the refrigerant filling the internal space in the sealed container 132 is sucked. After being sucked from the suction port 165 of the muffler 164 and sucked and compressed in the compression chamber 163, it is discharged to the outside of the sealed container 132 through the discharge thin tube 169 and the discharge tube 170 which is a discharge pipe provided in the sealed container 132. Is done.

  Further, the cooling compressor 120 stores mineral oil as refrigeration oil (not shown) in the lower part of the hermetic container 180 in the same manner as the cooling / warming compressor 106, and an electric compression element 182 is disposed. The electric compression element 182 is elastically supported on the bottom of the hermetic container 180 via a coil spring 181, and has a reciprocating type configuration in which a piston 184 is reciprocally fitted in the cylinder 186.

  Thus, in the cooling compressor 120 and the cooling compressor 106 of the present embodiment, the internal space of the sealed containers 132 and 180 is on the low pressure side of the cooling and heating cycle 115 and the cooling cycle 126 and is compressed by the electric compression element. This is an internal low-pressure compressor in which the refrigerant path after the operation is on the high-pressure side of the cooling and heating cycle 115.

  Here, the reciprocating direction of the piston 154 of the cooling / warming compressor 106 and the reciprocating direction of the piston 184 of the cooling compressor 120 are substantially parallel, and the pistons 154 and 184 of the cooling / warming compressor 106 and the cooling compressor 120. Is placed on the back side of the vending machine.

  Therefore, the fins (not shown) provided in the integrated heat exchanger 119 including the cold-temperature compressor 106, the cooling compressor 120, and the outdoor heat exchanger 110 are arranged so as to be substantially parallel to each other. .

  Further, the longitudinal direction of the integrated heat exchanger 119 including the outdoor heat exchanger 110 and the condenser 125 is positioned in a substantially vertical direction with respect to the reciprocating direction of the pistons 154 and 184 of the cooling compressor 106 and the cooling compressor 120. ing.

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

  When the cooling / warming switching chamber 101 is cooled, the refrigerant discharged from the cooling / warming compressor 106 passes through the four-way valve 111 and is condensed and liquefied by the outdoor heat exchanger 110 as shown by a dotted arrow in FIG. The liquid refrigerant discharged from the outdoor heat exchanger 110 is decompressed by the cooling capillary tube 112 through the dryer 114 and the cooling check valve 127, and is supplied to the indoor heat exchanger 108. Then, the refrigerant evaporated in the indoor heat exchanger 108 passes through the four-way valve 111 and is returned to the cool / warm compressor 106.

  At this time, for example, when pulling down at an outside air temperature of 30 ° C., it is usually necessary to cool at about 300 W. In this case, the cold compressor 106 is controlled so as to continuously operate at a high speed under pressure conditions of an evaporation temperature of about -30 ° C and a condensation temperature of about 50 ° C. As the temperature in the cooling / warming switching chamber 101 decreases, the rotation speed of the cooling / warming compressor 106 is sequentially decreased to adjust the capacity.

  Next, when the cooling / heating switching chamber 101 is heated, the refrigerant discharged from the cooling compressor 106 switches the flow path by the four-way valve 111 as shown by the solid line arrow in FIG. At 108, the liquid is condensed. The liquid refrigerant discharged from the indoor heat exchanger 108 is decompressed by the heating capillary tube 113 and supplied to the outdoor heat exchanger 110 through the heating check valve 128. Then, the refrigerant evaporated in the outdoor heat exchanger 110 switches the flow path by the four-way valve 111 and returns to the cool / warm compressor 106.

  At this time, for example, when pulling up at an outside air temperature of 15 ° C., it is usually necessary to heat at about 400 W. In this case, the cold compressor 106 is controlled to operate continuously under pressure conditions of an evaporation temperature of about 5 ° C. and a condensation temperature of about 65 ° C. As the temperature in the cooling / warming switching chamber 101 increases, the rotational speed of the cooling / warming compressor 106 is sequentially decreased to adjust the capacity.

  On the other hand, in the cooling cycle 126, the refrigerant discharged from the cooling compressor 120 is condensed and liquefied by the condenser 125. The liquid refrigerant discharged from the condenser 125 is decompressed by the expansion valve 123 and the second expansion valve 124 and supplied to the evaporator 121 and the second evaporator 122, respectively. Then, the refrigerant evaporated in the evaporator 121 and the second evaporator 122 is returned to the cooling compressor 120.

  At this time, the storage chamber 104 that has reached a predetermined temperature among the cooling dedicated chamber 102 and the second cooling dedicated chamber 103 closes the expansion valve 123 and the second expansion valve 124 to stop the supply of the refrigerant. . Further, when all the storage chambers 4 reach a predetermined temperature, the operation of the cooling compressor 120 is stopped.

  Here, when the cooling compressor 120 is operated together with the cooling compressor 106, the fin temperature around the path connected to the cooling cycle 126 becomes high. Therefore, when the cooling and heating cycle 115 is heated and when the cooling cycle 126 is operated simultaneously, cascade heat exchange can be performed via the fins of the outdoor heat exchanger 110 and the condenser 125, and the condenser 125 The warmed air can be sucked into the outdoor heat exchanger 110 acting as an evaporator, and the cooling and heating cycle 115 can be operated at a high evaporation temperature of about 0 ° C. to 10 ° C. Thereby, the compression ratio of the cooling / heating cycle 115 can be reduced, the efficiency of the cooling / heating compressor 106 can be improved, and the power consumption can be reduced.

  Thus, when the cooling / heating switching chamber 101 is heated, the evaporating temperature is higher than when the cooling / heating switching chamber 101 is cooled. Circulation amount increases. When the refrigerant circulation amount increases in this way, for example, a valve mechanism (not shown) such as a suction lead that is a suction side valve or a discharge lead that is a discharge side valve provided in the refrigerant flow path in the cold temperature compressor 106. ) Stress and impact, and the valve open / close distance increases, and the burden on the valve increases. In addition, a large amount of refrigerant is compressed to increase the load during compression, so that the crankshaft 150, the bearing 146, etc. The sliding condition becomes severe, and there is a concern that the reliability may be lowered.

  However, in the present embodiment, the R600a refrigerant capable of greatly reducing the high pressure is used, and the maximum operating speed during the heating operation is further reduced with respect to the maximum operating speed during the cooling operation of the cooling compressor 106. Further, by setting these ratios in the range of 0.7 to 0.9 in accordance with the rate of increase in the refrigerant circulation amount, the cylinder head 154 is prevented by preventing the refrigerant circulation amount from being excessive in the cooling and heating cycle 115. It is possible to improve the reliability of the cool / warm compressor 106 by preventing breakage of sliding parts such as valves provided inside the compressor.

  Specifically, for example, even when the rotation frequency during the cooling operation is 72 rps at the maximum speed, the maximum rotation frequency during the heating operation is 80% of the maximum rotation speed 72 rps during the cooling operation (the maximum rotation during the cooling operation). The ratio of the maximum number of revolutions during the heating operation with respect to the number is set to, for example, about 54 rps, which is equal to or less than 60 rps, which is 0.8), so that it is possible to prevent an excessive amount of refrigerant circulation. In this case, preferably, the maximum rotation frequency during the heating operation is preferably 80% or less of the maximum rotation number during the cooling operation. However, the maximum rotation frequency during the cooling operation may be reduced depending on design conditions. In the case where it is suppressed, the reliability can be ensured even if it is 90% or less (the ratio of the maximum rotational speed during the heating operation to the maximum rotational speed during the cooling operation is 0.9).

  Also, if the refrigerant circulation rate is too small, it will not be possible to secure the refrigeration capacity under high load conditions during heating, and it will not be possible to sufficiently heat during heating operation. The lower limit of the maximum rotational speed ratio during the heating operation is desirably about 0.7, and it is necessary to secure at least 0.5 or more.

  Further, the ratio of the maximum rotational speed to the minimum rotational speed during heating is desirably 2.0 or less. For example, when the minimum rotational speed during heating is 29 rps as in the present embodiment, the maximum It is desirable to operate at a rotational speed of 58 rps or less, which is twice the minimum rotational speed.

  Regarding the setting of the maximum operation speed during the heating operation, the heating operation is performed so that the refrigerant circulation rate at the maximum operation rotation rate during the heating operation is close to the refrigerant circulation rate at the maximum operation rotation number during the cooling operation. If the maximum operation speed during operation is lower than the maximum operation speed during cooling operation, the amount of refrigerant circulation increases due to the heating operation with a high evaporation temperature, and the stress applied to the valve provided in the electric compression element In addition to increasing the impact and valve opening / closing distance and increasing the load on the valve, the load on compression increases due to the compression of a large amount of refrigerant, resulting in severe sliding conditions such as crankshafts and bearings. It is possible to provide a reliable cooling and heating cycle.

  As described above, it is not always necessary to adjust the refrigerant circulation amount at the maximum operation rotation speed during the heating operation and the refrigerant circulation amount at the maximum operation rotation speed during the cooling operation to an approximate range by design. If the amount can be maintained in an approximately equivalent range, there is no need to consider the design of the valve mechanism and sliding mechanism with high load resistance in advance in preparation for an increase in load during heating operation. This is advantageous both in terms of cost and design standardization.

  The degree to which the refrigerant circulation amount is approximated is that the difference between the refrigerant circulation amount at the maximum operation speed during the heating operation and the refrigerant circulation amount at the maximum operation speed during the cooling operation is the maximum operation speed during the cooling operation. Within the range of ± 10% of the refrigerant circulation amount, it is advantageous from the viewpoint of maintaining a good balance between the above-described reliability and heating capability.

  As described above, in the present embodiment, even when cooling and heating are realized by a single cold compressor 106, the internal temperature of the cold compressor 106 can be increased by using the R600a having a very high high pressure. In addition, it is possible to ensure the load resistance and durability of the high-pressure piping, and to suppress the temperature rise inside the cold / hot compressor 106.

  Further, in the heating operation, which is a severe condition in terms of reliability of the cooling / compressing compressor 106 because the highest pressure is the highest among the operating conditions of the cooling / heating cycle 115, the inverter is driven to drive the cooling / heating compressor 106. By making the maximum operation speed lower than the maximum operation speed during the cooling operation, it becomes possible to further improve the reliability during the heating operation.

  In addition, it is possible to achieve a heating efficiency that is twice as high as that of a heating means such as an electric heater that has a heating efficiency of about 1. Further, the inverter is driven in both the cooling operation and the heating operation. By operating the cold-temperature compressor 106 at a high load, the compressor can be operated at a high rotational speed to increase the refrigeration capacity, and at a low load, it can be continuously operated at a low rotational speed, thereby greatly reducing power consumption. Can be achieved.

  Further, in the present embodiment, since the cool / warm compressor 106 is installed in the cover 105, it is possible to prevent a temperature drop of the cool / warm compressor 106 as a whole at a low outside air temperature. Accordingly, since it is possible to prevent the intake gas temperature of the cool / warm compressor 106 from being lowered, the efficiency of the cool / warm compressor 106 can be prevented from being lowered and the high cycle efficiency of the cooling / heating cycle 115 can be maintained.

  Further, in the present embodiment, an air path as shown by a solid arrow in FIG. 3 is formed so as to dissipate heat from the condenser 125, but the cold / high temperature compressor 106 is installed in the cover 105. The entire temperature drop is suppressed without being affected by the air path, and higher cycle efficiency can be maintained.

  Moreover, since the outdoor heat exchanger 110 and the condenser 125 which are constituted by a two-pass fin tube heat exchanger are integrated via fins, the cooling and heating cycle 115 and the cooling cycle 126 and the respective pipes are connected. Influenced by vibrations.

  In particular, in an internal high-pressure type compressor such as a rotary type and a scroll type that are generally installed in conventional vending machines, the electric compression element is directly fixed to the sealed container, so that vibration due to compression is transferred to the sealed container. Since the vibration is directly transmitted and the vibration of the pipe tends to increase. When two compressors are shared by one heat exchanger, there is a concern about the breakage of the pipe caused by these vibrations. It had been.

  In particular, under a heating condition in which the compression load becomes very large, vibration due to compression further increases, and further deterioration in reliability due to vibration becomes a problem.

  However, according to the present embodiment, the cold compressor 106 and the cooling compressor 120 are internal low-pressure types, and the electric compression elements 140 and 182 are elastic members such as coil springs 142 and 181 with respect to the sealed containers 132 and 180. The vibration of the electric compression elements 130 and 182 generated by the reciprocating motion of the pistons 154 and 184 does not directly propagate to the sealed containers 132 and 180, and the coil is elastically supported by the coil. Since it can be reduced by the spring 132, vibration transmission to the pipe can be reduced, and even if the pipes of the two compressors are connected to one outdoor heat exchanger 110 and the condenser 125, the vibration of the pipes can be reduced. Since this can prevent the pipe from being broken, it is possible to prevent a decrease in reliability due to vibration, and the outdoor heat exchanger 110 and the condensation can be prevented. The benefits of high efficiency surface of the integrated condenser consisting of 125 can be utilized sufficiently.

  Furthermore, the cold compressor 106 and the cooling compressor 120 of the present embodiment are the pistons 154 and 184 and the compression chambers 163 that have large vibrations to compress the refrigerant in the lower part of the electric compression element. Since 187 is arranged in the upper part, the compression chambers 163 and 187, which are the vibration sources of the compressor, are further away from the coil spring that elastically supports the electric compression element 130 to the hermetic container, thereby further reducing vibration. It becomes possible.

  Therefore, it is possible to provide a highly reliable vending machine that prevents a decrease in reliability due to vibrations and that has a high heat exchange capability.

  Furthermore, since the reciprocating directions of the two compressors are not located on the same extension line by making the reciprocating directions of the pistons 154 and 184 substantially parallel with each other, the reciprocating directions of the two compressors 154 and 184 are the same. The vibration caused by the reciprocating motion of the piston 154 that is a vibration source is prevented from resonating or amplifying by two compressors, and pipe breakage due to abnormal vibration when a plurality of reciprocating compressors are arranged in the vicinity. Reliability degradation can be prevented.

  In addition, the pistons 154 and 184 of the cold-temperature compressor 106 and the cooling compressor 120 are installed so as to be positioned on the back side of the vending machine, and the outdoor in a substantially vertical direction with respect to the reciprocating direction of the pistons 154 and 184 By positioning the longitudinal direction of the heat exchanger 110 and the condenser 125, fins 119 a provided in the integrated heat exchanger 119 including the cold compressor 106, the cooling compressor 120, and the outdoor heat exchanger 110 are provided. Are arranged so as to be substantially parallel to each other, so that an air passage from the back side of the vending machine to the door 129 side is easily formed like the air passage shown by the arrow in FIG. Even when the vibration in the reciprocating direction is transmitted among the vibrations of the machine 106 and the cooling compressor 120, the fin 119a is vibrated in a direction substantially parallel to the arrangement direction of the fin 119a. Less susceptible to air resistance around due to movement, thereby reducing the vibration and noise from the fins 119a.

  In addition, vibration generated when the refrigerant is compressed is transmitted to the fin 119a of the integrated heat exchanger 119 including the outdoor heat exchanger 110 and the condenser 125 through two paths, and is caused by the vibration of the fin 119a. Since abnormal noise can be prevented, a low-noise and low-vibration vending machine can be provided.

  In addition, since the cold compressor 106 and the cooling compressor 120 are always operated at different operating frequencies, the frequency that is the main component of pressure pulsation is always different. Therefore, it is possible to prevent the vibration of the piping in the cooling / heating cycle 115 and the cooling cycle 126 from resonating and increase in vibration, and to reduce the vibration transmission of the vending machine.

  Furthermore, since the contact surface A between the leg 172 and the elastic member 174 of the cool / warm compressor 106 of the present embodiment is located above the lower end surface 132a of the hermetic container 132, The distance C between the center of gravity B in the direction and the contact surface A between the leg 172 of the cooling compressor 106 and the elastic member 174 that elastically supports the leg 172 is equal to the center B of the cooling compressor 106 in the vertical direction and the sealed container It is shorter than the distance D from the lower end surface 132a of 132.

  As a result, the vibration amplitude of the cooling / compressing compressor 106 is the smallest in the vicinity of the center of gravity B and increases as the distance from the center of gravity B increases. Therefore, the leg 172 and the elastic member are located closer to the center of gravity B of the cooling / compressing compressor 106. By positioning the contact surface A with the 174, the vibration of the entire compressor 106 for cooling and cooling can be reduced, and further, the transmission of vibration to the vending machine can be reduced. It is possible to provide a high-quality vending machine that does not generate noise.

  In the present embodiment, the positional relationship between the center of gravity of the compressor and the contact surface between the leg and the elastic member is defined for the cooling / compressing compressor 106, but may be defined similarly for the cooling compressor 120. Good.

  Further, in the present embodiment, the internal low pressure type in which the pressure in the sealed container 132 of the cooling / heating compressor 106 is equivalent to the low pressure of the cooling and heating cycle 115 is used, and the inside of the sealed container 132 is a high pressure type. Since the amount of the refrigerant dissolved in the refrigerating machine oil 134 can be reduced compared to the case of the above, the amount of the R600a that is a combustible refrigerant enclosed in the cooling and heating cycle 115 can be suppressed. Since the absolute amount at the time of leakage can be reduced and the amount of flammable refrigerant held in the system can be reduced, the explosion-proof safety can be improved.

  Further, in the present embodiment, the cooling compressor 120 is also an internal low pressure type like the cooling temperature compressor 106, and the amount of R600a enclosed in the cooling cycle 126 is suppressed similarly to the cooling heating cycle 115. Needless to say, it is possible to improve safety.

  In addition, if R600a, which is a flammable refrigerant, is also enclosed in the cooling cycle 126, it is possible to provide an environmentally friendly vending machine that further contributes to the prevention of global warming, and the same refrigerant as the cooling and heating cycle 115 is applied. There are also manufacturing and service advantages.

  In addition, since the vending machine is cooled and heated by a system separated into two independent circuits of the cooling cycle 126 and the cooling and heating cycle 115, all refrigerants can be used even in the event of a leak of flammable refrigerant. However, it is not subject to leakage, and a certain safety factor can be expected for the explosion-proof safety of vending machines suitable for combustible refrigerants.

  As described above, in the present embodiment, the application product is a vending machine that can be cooled or heated, but the main configuration that is characteristic only needs to be in the form of a refrigerating apparatus that can be heated. Applicable products are not limited to vending machines. Furthermore, if a specific configuration and conditions are limited, the compressor can be characterized.

  In the present embodiment, the expression “cooling / heating cycle” means the cooling / heating cycle or the cooling / heating cycle, and the expression “cooling / heating switching room” is the cooling / heating switching room or the cooling / heating cycle. It means the switching chamber, and the expression “cooling / heating compressor” means a cooling / heating compressor or a cooling / heating compressor.

(Embodiment 2)
FIG. 5 is a longitudinal sectional view of a cooling compressor according to Embodiment 2 of the present invention, FIG. 6 is a longitudinal sectional view of the cooling compressor according to the embodiment, and FIG. 7 is a cooling temperature according to the embodiment. 8 is an exploded perspective view around the suction lead and the discharge lead of the compressor, FIG. 8 is a diagram showing the correlation between the plate thickness of the suction lead and the stress of the embodiment, and FIG. 9 is the discharge of the embodiment It is a figure which shows the comparison of the impact fatigue strength of a lead | read | reed.

  In the present embodiment, the cooling compressor and the internal structure of the cooling / heating compressor provided in the cooling cycle 126 and the cooling / heating cycle 115 described in Embodiment 1 will be described in detail. Detailed description of the contents overlapping with those in FIG.

  In the figure, the cooling compressor 120 stores mineral oil as refrigerating machine oil (not shown) in the lower part of the sealed container 180, and R600a is sealed as a refrigerant in the internal space 180a. In contrast, the electric compression element 182 is elastically disposed. The electric compression element 182 is elastically supported on the bottom of the hermetic container 180 via a coil spring 181, and has a reciprocating type configuration in which a piston 184 is reciprocally fitted in the cylinder 186.

  The electric compression element 182 includes a stator 192 fixed below the block 190 and a rotor 194 fixed below the main shaft portion 193a, and forms an induction electric motor driven at a constant speed. It is operated at the same operating frequency as the commercial power supply frequency.

  The electric compression element 182 includes a block 190 that forms a cylinder 186, a piston 184 that is reciprocally fitted in a bore hole 186a of the cylinder 186, and a main shaft portion 193a that is pivotally supported by a bearing 195 of the block 190. A crankshaft 193 composed of a core shaft portion 193b and a connecting rod 185 that connects the eccentric shaft portion 193b and the piston 184 are provided, and the rotational motion of the crankshaft 193 is converted into the reciprocating motion of the piston 184.

  Further, the space volume of the compression chamber 187 formed between the piston 184 and the bore hole 186a is increased or decreased by the reciprocating motion of the piston 184, so that the refrigerant filling the internal space 180a in the sealed container 180 is After being sucked in from a suction port (not shown) of a suction muffler 196 and sucked and compressed in a compression chamber 187 through a suction valve 197, it was provided in a discharge thin tube 199 and a sealed container 180 through a discharge valve 198. It is discharged out of the sealed container 132 through a discharge tube 200 which is a discharge pipe.

  As described above, in the cooling compressor 120 of the present embodiment, the internal space 180a of the sealed container 180 is on the low pressure side of the cooling cycle 126, and the refrigerant path after being compressed by the electric compression element 182 is the cooling cycle 126. This is an internal low-pressure type compressor that is on the high-pressure side.

  Next, the configuration of the cold / hot compressor 106 will be described.

  A mortar-shaped lower container 130 formed by deep drawing of a rolled steel plate and an inverted mortar-shaped upper container 131 are engaged, and the engagement portion is welded all around to form a sealed container 132. Mineral oil is stored as the refrigerating machine oil 134 in the lower part of the sealed container 132, and R600a is sealed as a refrigerant in the inner space 132 b, and the electric compression element 140 is elastically disposed with respect to the sealed container 132. ing. The electric compression element 140 is elastically supported on the bottom of the hermetic container 132 via a coil spring 142.

  The electric compression element 140 includes a stator 146 fixed below the block 144 and connected to an inverter drive circuit (not shown), and a rotor 150 containing a permanent magnet and fixed below the main shaft portion 148. The inverter driving electric motor is formed, and is driven by the inverter driving circuit at a plurality of operating frequencies including the operating frequency exceeding the commercial power supply frequency.

  The electric compression element 140 includes a block 144 that forms a cylinder 152, a piston 154 that is reciprocally inserted into a bore hole 153 of the cylinder 152, and a main shaft portion 148 that is pivotally supported by a bearing 156 of the block 144. A crankshaft 160 composed of a core shaft portion 158 and a connecting rod 162 connecting the eccentric shaft portion 158 and the piston 154 are provided, and the rotational motion of the crankshaft 160 is converted into the reciprocating motion of the piston 154.

  Further, the space volume of the compression chamber 163 formed between the piston 154 and the bore hole 153 is increased or decreased by the reciprocating motion of the piston 154, so that the refrigerant in the sealed container 132 flows from the suction port 165 of the suction muffler 164. After being sucked and sucked into the compression chamber 163 through the suction hole 202 of the valve plate 201 via the suction lead 167 and compressed by the reciprocating motion of the piston 154, the discharge lead 168 passes through the discharge hole 203 of the valve plate 201. Through the discharge thin tube 169 and the discharge tube 170 which is a discharge pipe provided in the closed container 132, and is discharged out of the sealed container 132.

  Here, the plate thickness of the suction lead 167 of the cooling compressor 106 is 0.254 mm, and the ratio of the suction lead 197 of the cooling compressor 120 to the plate thickness of 0.203 mm is 1.25. At this time, the spring constant of the suction lead 197 of the cooling compressor 120 is about 290 N / m, whereas the spring constant of the suction lead of the cooling compressor 106 is about 570 N / m, which is approximately 2 About 0 times.

  The discharge lead 168 is fixed to the valve plate 201 by a caulking pin 206 together with a spring lead 204 having elasticity that restricts the opening amount of the discharge lead 168 and a stopper 205 having no rigidity and high rigidity. Seals in contact with a discharge valve seat 208 formed around the discharge hole 203 of 201. Furthermore, the discharge lead 168 of the cooling compressor 106 has higher impact fatigue strength than the discharge lead 198 of the cooling compressor 120, and in this embodiment, the discharge lead 198 of the cooling compressor 120 is high. However, the discharge lead 168 of the cool / warm compressor 106 is made of stainless valve steel, so that the impact fatigue strength of the discharge lead 168 of the cool / warm compressor 106 is less than that of the material used for cooling. Compared with the discharge lead 198 of the compressor 120, it is improved by about 25%.

  The composition of the valve steel and stainless valve steel is shown in (Table 1).

  As shown in (Table 1), the biggest feature of stainless valve steel is that it contains chromium and molybdenum, which valve steel does not contain, and the tensile strength due to this material difference is almost the same. However, as shown in FIG. 9, the impact speed against fatigue fracture, that is, the impact fatigue strength, is about 25% higher in the stainless steel valve steel.

  As described above, in the compressor according to the present embodiment, attention is paid to the impact fatigue strength among a plurality of items considered to improve the reliability of the discharge lead 168 when performing the heating operation, and the impact fatigue strength. Is used for the discharge lead 168 of the cold / hot compressor 106.

  The operation of the vending machine configured as described above will be described below. In the present embodiment, a case where the cooling operation by the cooling cycle 126 and the heating operation by the cooling heating cycle 115 are simultaneously moved will be described as an example.

  When the cooling compressor 120 is operated together with the cooling compressor 106, the path of the outdoor heat exchanger 110 connected to the cooling cycle 126 acts as a condenser, and the fin temperature around the path becomes high. Therefore, when the cooling cycle 115 is heated and when the cooling cycle 126 is operated simultaneously, cascade heat exchange can be performed via the fins of the outdoor heat exchanger 110, and the atmosphere heated by the condenser can be exchanged. The cooling and heating cycle 115 can be operated at a high evaporation temperature of about 0 ° C to 10 ° C. Thereby, the compression ratio of the cooling / heating cycle 115 can be reduced, the efficiency of the cooling / heating compressor 106 can be improved, and the power consumption can be reduced.

  Further, when the cooling / warming switching chamber 101 is heated, the evaporation temperature is higher than when the cooling / warming switching chamber 101 is cooled, so that the density of the refrigerant is increased and the refrigerant circulation amount in the cooling / warming cycle 115 is increased. Will increase. Furthermore, since the cooling / heating compressor 106 is driven even at a high operating frequency exceeding the commercial power source, the amount of refrigerant circulating in the cooling / heating cycle 115 increases.

  As described above, when the refrigerant circulation amount increases, the opening amount of the suction lead 167 greatly increases when the refrigerant is sucked into the compression chamber 163, the stress applied to the suction lead 167 increases, and the reliability of the suction lead 167 increases. In the present embodiment, the cooling compressor 120 having the thickness of the suction lead 167 of the cold-temperature compressor 106 is focused on the technical problem that the load of the suction lead, which is greatly influenced by the refrigerant circulation amount, becomes large. The ratio of the suction lead 197 to the plate thickness is 1.25.

  As a result, as shown in FIG. 8, the maximum stress during cooling of the suction lead 197 used in the cooling compressor 120 with a plate thickness of 0.203 mm is 1.0 ("cooling for cooling / cooling for cooling / When the lead having the same thickness of 0.203 mm is used for the heating operation, “Lead at the time of cooling / t0.203” in FIG. 8 is used. As shown in FIG. 2, the maximum stress applied to the suction lead increases to about 1.2 times, and the reliability of the suction lead decreases.

  On the other hand, in the suction lead 167 of the cold compressor 106 according to the present embodiment in which the plate thickness of the suction lead is 0.254 mm, “Cooling warming / Lead t0.254” at the lower right of FIG. Thus, the maximum stress during heating can be reduced more than the maximum stress during cooling.

  Thus, in this embodiment, the plate thickness of the suction lead 167 of the cooling compressor 106 is 0.254 mm, and the ratio of the suction lead 197 of the cooling compressor 120 to the plate thickness of 0.203 mm is 1.25. At this time, the spring constant of the suction lead 197 of the cooling compressor 120 is about 290 N / m, whereas the spring constant of the suction lead of the cold compressor 106 is about 570 N / m, which is approximately Since the refrigerant circulation amount is larger than that in the cooling operation, the maximum stress generated in the suction lead 167 is reduced even during the heating operation in which the load on the suction lead is increased. In addition, breakage of the suction lead 167 can be prevented, and the reliability of the cold / high temperature compressor 106 can be improved.

  In the present embodiment, the ratio of the plate thickness of the suction lead 167 of the cooling compressor 106 to the plate thickness of the suction lead 197 of the cooling compressor 120 is 1.25, but the load on the suction lead is Considering the increase, the reliability of the suction lead 167 can be ensured by setting the cooling compressor 120 to at least 1.20 times. However, as the plate thickness is increased, the response of the suction lead 167 tends to decrease. In the so-called difficult-to-open suction lead 167 whose response is decreased in this way, the suction efficiency of the refrigerant is reduced and the compression is reduced. Therefore, if the plate thickness of the suction lead 167 of the cooling compressor 106 is at least 2.0 times or less than the suction lead 197 of the cooling compressor 120, the response followability can be improved. Achieving the intended purpose by avoiding a fatal effect, and more preferably 1.5 times or less in order to achieve a balance between stress resistance and response tracking I have confirmed that.

  The ratio of the spring constant of the suction lead 167 of the cooling compressor 106 to the spring constant of the suction lead 197 of the cooling compressor 120 is about 2.0 times, but considering the increase in the load on the suction lead The reliability of the suction lead 167 can be ensured by setting at least 1.5 times the cooling compressor 120. In addition, regarding the upper limit of the spring constant, the responsiveness of the suction lead 167 tends to decrease as the spring constant increases in the same way as the above-described plate thickness. In the suction lead 167, there is a concern that the suction efficiency of the refrigerant is lowered and the capacity of the compressor is lowered. Therefore, the plate thickness of the suction lead 167 of the cooling / warming compressor 106 is larger than the suction lead 197 of the cooling compressor 120. If it is at least 3.0 times or less, it will be possible to avoid the fatal effect on response tracking and achieve the intended purpose, and also to balance stress resistance and response tracking while maintaining a balance. Then, it has been confirmed that it is more desirable to make it 2.5 times or less.

  Further, regarding this spring constant, it is possible to increase the spring constant by increasing the plate thickness, and it is also possible to increase the spring constant by devising the shape of the suction lead 167.

  Further, the opening amount of the discharge lead 168 is regulated by the spring lead 204 and the stopper 205 unlike the suction lead 167 which does not regulate the opening amount.

  Therefore, if the refrigerant circulation amount increases during the heating operation, the amount of refrigerant passing through the discharge hole 203 per unit time increases, so that the impact force that the discharge lead 168 collides with the spring lead 204 and the stopper 205 that regulates the opening amount. The impact force that collides with the discharge valve seat 208 when the discharge lead 168 is closed increases. In this embodiment, the discharge lead 168 of the cooling / warming compressor 106 is the discharge lead 198 of the cooling compressor 120. The impact fatigue strength is higher than that of the discharge lead 198 of the compressor 120 for cooling, and valve steel is used for the discharge lead 198 of the compressor 120 for cooling. Stainless steel valve steel is used for the discharge lead 168 of the compressor 106 for cooling and cooling. Thus, the impact fatigue strength of the discharge lead 168 of the cooling compressor 106 is approximately the same as that of the discharge lead 198 of the cooling compressor 120. About 5 percent are improved.

  Therefore, the impact force that collides with the spring lead 204 and the stopper 205, which is the opening amount regulating means of the discharge lead 168, and the impact force that collides with the discharge valve seat 208 when the discharge lead 168 closes as the refrigerant circulation amount increases. Even in this case, the reliability of the discharge lead 168 can be ensured.

  In addition, the impact fatigue strength is improved by approximately 20% or more compared to that of the discharge lead of the cooling compressor 120 by adjusting the content of chromium and molybdenum, which are the material composition of the stainless valve steel. By doing so, the desired effect can be obtained.

  In this way, particularly in the cold compressor 106 in which the refrigerant circulation amount increases in the heating operation, the load on the discharge lead 168 due to the impact force when the discharge lead 168 collides with other parts due to the influence of the refrigerant circulation amount is large. Focusing on the technical problem such as, the reliability of the discharge lead 168 is improved by improving the impact resistance strength of the discharge lead 168 at the time of heating in which the refrigerant circulation amount increases as compared with the time of cooling. The reliability of the compressor 106 can be improved.

  In the present embodiment, the spring lead 204 having elasticity and the stopper 205 having no elasticity are used as the opening amount regulating means of the discharge lead 168. However, the spring lead 204 is the stopper 205 of the discharge lead 168. This is not necessarily required because it is provided to alleviate the impact force to the nozzle and improve the delay in closing the discharge lead 168 and improve the response. As a means for restricting the opening amount of the discharge lead 168, the stopper 205 alone can be used.

  If the combination of the cooling compressor 120 and the cooling compressor 106 does not employ the spring lead 204, it cannot be expected to alleviate the impact force of the discharge lead 168 of the spring lead 204, so substantially equivalent to 20%. A measure for improving the impact fatigue strength that exceeds this is required.

  As described above, in the present embodiment, the stress resistance and shock fatigue strength around the valve mechanism such as the suction lead 167 and the discharge lead 168 provided in the cold compressor 106 are increased to prevent the sliding parts from being damaged. In addition, the reliability of the cold / hot compressor 106 can be improved.

  Further, in order to prevent a decrease in the reliability of the suction lead 167 and the discharge lead 168 accompanying the increase in the amount of refrigerant circulation during the heating operation, the cooling / heating compressor 106 has a higher rotational speed than that during the cooling operation. It is also an effective means to set the maximum operating rotational speed during the warming operation low.

  Specifically, for example, even when the rotation frequency during the cooling operation is 72 rps at the maximum speed, the maximum rotation frequency during the heating operation is 80% of the maximum rotation speed 72 rps during the cooling operation (the maximum rotation during the cooling operation). The ratio of the maximum rotational speed during the heating operation to the number is 0.8), which is 60 rps or less, for example, about 54 rps, so that it is possible to prevent the refrigerant circulation amount from being excessive. In this case, preferably, the maximum rotation frequency during the heating operation is preferably 80% or less of the maximum rotation number during the cooling operation. However, the maximum rotation frequency during the cooling operation may be reduced depending on design conditions. In the case where it is suppressed, the reliability can be ensured even if it is 90% or less (the ratio of the maximum rotational speed during the heating operation to the maximum rotational speed during the cooling operation is 0.9).

  Also, if the refrigerant circulation rate is too small, it will not be possible to secure the refrigeration capacity under high load conditions during heating, and it will not be possible to sufficiently heat during heating operation. The lower limit of the maximum rotational speed ratio during the heating operation is desirably about 0.7, and it is necessary to secure at least 0.5 or more.

  Further, the ratio of the maximum rotational speed to the minimum rotational speed during heating is desirably 2.0 or less. For example, when the minimum rotational speed during heating is 29 rps as in the present embodiment, the maximum It is desirable to operate at a rotational speed of 58 rps or less, which is twice the minimum rotational speed.

  Further, in the present embodiment, cooling compressor 120 is installed on the air passage (the air passage shown by the solid line arrow in FIG. 3) for forcibly cooling the inside of the machine room by machine room fan 210. Since the cool / warm compressor 106 is installed in a place other than the air passage, it is possible to prevent a decrease in the intake gas temperature of the cool / warm compressor 106 especially at a low outside air temperature when the cool / warm compressor 106 performs the heating operation. Therefore, the cycle efficiency of the cooling and heating cycle during the heating operation can be increased, and the power consumption of the vending machine can be reduced.

  Furthermore, in the present embodiment, since the cool / warm compressor 106 is installed in the cover 105, it is possible to prevent the temperature of the cool / warm compressor 106 from being lowered at a low outside air temperature. Accordingly, since it is possible to prevent the intake gas temperature of the cool / warm compressor 106 from being lowered, the efficiency of the cool / warm compressor 106 can be prevented from being lowered and the high cycle efficiency of the cooling / heating cycle 115 can be maintained.

  In the present embodiment, the material of the cover 105 that covers the cool / warm compressor 106 is not particularly limited. However, by using the cover 105 as a heat-insulating cover having heat insulation properties, the cool / warm compressor can be used at a low outside temperature. The temperature decrease of the entire 106 can be prevented to a higher degree. Accordingly, since it is possible to prevent the intake gas temperature of the cool / warm compressor 106 from being lowered, the efficiency of the cool / warm cycle 115 can be further improved by preventing the cool temperature compressor 106 from being lowered in efficiency.

  In the present embodiment, the torque of the electric motor for the inverter provided in the cool / heat compressor 106 is the cooling power when the cool / heat compressor 106 is operating at the maximum number of revolutions during the cooling operation. In the state where the compressor 120 is operating at the maximum rotation speed, the torque of the induction motor provided in the cooling compressor 120 is made larger than that of the cooling compressor 120. In the cooling / heating compressor 106 in which the refrigerant circulation amount increases in the temperature operation, even when the load of the electric motor increases with an increase in the refrigerant circulation amount, the electric motor in which the torque at the time of higher load becomes larger is used. Since the reliability of the cool / warm compressor 106 can be further improved by providing it in 106, a vending machine with improved reliability can be provided.

  In order to increase the current value flowing through the stator winding, as a means for increasing the torque of the cold-temperature compressor 106, for example, the current value is increased by shortening the winding length of the stator, and the torque However, if the winding length is shortened, the efficiency of the electric motor tends to decrease. Therefore, in the present embodiment, a larger current is allowed to flow only at high loads in the inverter operation. The torque is increased by controlling in this way.

  As described above, in the present embodiment, the application product is a vending machine that can be cooled or heated, but the main configuration that is characteristic only needs to be in the form of a refrigerating apparatus that can be heated. Applicable products are not limited to vending machines. Furthermore, if a specific configuration and conditions are limited, the compressor can be characterized.

  In the present embodiment, the expression “cooling / heating cycle” means the cooling / heating cycle or the cooling / heating cycle, and the expression “cooling / heating switching room” is the cooling / heating switching room or the cooling / heating cycle. It means the switching chamber, and the expression “cooling / heating compressor” means a cooling / heating compressor or a cooling / heating compressor.

  As described above, since the vending machine according to the present invention can greatly reduce power consumption and has high reliability, the vending machine can be applied to equipment having a refrigeration apparatus that can be heated, such as a showcase or a cup vending machine.

Refrigerant circuit diagram of vending machine in Embodiment 1 of the present invention The perspective view of the freezing apparatus which comprises the refrigerating cycle in the embodiment Plan sectional view of the compressor for cooling and cooling seen from above the vending machine in the same embodiment Longitudinal sectional view of a compressor for cooling / heating in the same embodiment Longitudinal sectional view of a cooling compressor in Embodiment 2 of the present invention Longitudinal sectional view of the cooling / heating compressor of the same embodiment Exploded perspective view around the suction and discharge leads of the cold compressor of the same embodiment The figure which shows correlation with the board thickness of the suction | inhalation lead of the same embodiment, and stress The figure which shows the comparison of the impact fatigue strength of the discharge lead of the embodiment Refrigerant circuit diagram of a conventional vending machine

Explanation of symbols

105 Cover 106 Cooling Compressor 115 Cooling Heating Cycle 120 Cooling Compressor 126 Cooling Cycle 126, 180 Sealed Container 167, 197 Suction Lead 168, 198 Discharge Lead 140, 182 Electric Compression Element 210 Machine Room Fan

Claims (13)

  Cooling cycle for cooling operation, cooling / heating cycle capable of switching between cooling operation and heating operation, cooling compressor provided in the cooling cycle, and cooling temperature provided in the cooling / heating cycle A compressor, and the cooling / warming compressor includes an airtight container and an electric compression element provided in the airtight container, and is an inverter compressor operated at a plurality of rotation speeds. A vending machine in which R600a is enclosed as a refrigerant in the temperature cycle, and the cooling and heating cycle is such that the maximum operation speed during the heating operation is lower than the maximum operation speed during the cooling operation.   The maximum operation speed during the cooling operation is changed to the maximum operation speed during the cooling operation, so that the refrigerant circulation amount at the maximum operation speed during the heating operation approximates the refrigerant circulation amount at the maximum operation speed during the cooling operation. The vending machine according to claim 1, wherein the vending machine is lower than the number.   Cooling operation is performed at the maximum operating rotational speed during the heating operation of the compressor for cooling and cooling to such an extent that the stress or impact applied to the valve mechanism provided in the electric compression element of the compressor for cooling and cooling during heating operation is alleviated. The vending machine according to claim 1, wherein the vending machine is lower than a maximum operating rotational speed at the time.   The maximum operating rotational speed at the time of the heating operation of the compressor for cooling / warming is lowered so that the ratio is 0.5 or more and 0.9 or less with respect to the maximum operating rotational speed at the time of cooling operation. The vending machine according to any one of the above.   Cooling cycle for cooling operation, cooling / heating cycle capable of switching between cooling operation and heating operation, cooling compressor provided in the cooling cycle, and cooling temperature provided in the cooling / heating cycle The cooling / heating cycle includes R600a as a refrigerant, and the cooling / warming compressor includes a hermetic container and an electric compression element provided inside the hermetic container. Inverter compressor that is operated at the number of revolutions, and the ratio of the thickness of the suction lead provided in the electric compression element to the thickness of the suction lead of the cooling compressor is 1.2 or more and 2 Vending machine thickened to be less than 0.0.   Cooling cycle for cooling operation, cooling / heating cycle capable of switching between cooling operation and heating operation, cooling compressor provided in the cooling cycle, and cooling temperature provided in the cooling / heating cycle The cooling / heating cycle includes R600a as a refrigerant, and the cooling / warming compressor includes a hermetic container and an electric compression element provided inside the hermetic container. The ratio of the spring constant of the suction lead provided in the electric compression element to the spring constant of the suction lead of the cooling compressor is 1.5 or more. Vending machine enlarged to be less than 0.0.   Cooling cycle for cooling operation, cooling / heating cycle capable of switching between cooling operation and heating operation, cooling compressor provided in the cooling cycle, and cooling temperature provided in the cooling / heating cycle The cooling / heating cycle includes R600a as a refrigerant, and the cooling / warming compressor includes a hermetic container and an electric compression element provided inside the hermetic container. And the ratio of the impact fatigue strength of the discharge lead provided in the electric compression element to the impact fatigue strength of the discharge lead of the cooling compressor is 1. .Vending machine enhanced to be 2 or more.   8. The valve lead is used for the material of the discharge lead provided in the electric compression element of the compressor for cooling, and the stainless steel valve steel is used for the material of the discharge lead provided for the electric compression element of the compressor for cooling and cooling. Vending machine.   In the state where the electric motor of the cooling / heating compressor is operating at the maximum number of revolutions during the cooling operation, the torque of the electric motor is at least the torque when the electric motor of the cooling compressor is operating at the maximum number of revolutions. The vending machine according to any one of claims 1 to 4, wherein the vending machine is configured to withstand a load caused by an increase in a refrigerant circulation amount during a heating operation of the cooling / warming compressor by setting it to be larger than that.   The cooling compressor is installed on an air passage that performs forced cooling in the machine room by a machine room fan, and the cooling / warming compressor is installed at a place other than the air passage. The vending machine according to one item.   The vending machine according to any one of claims 1 to 10, wherein a cover that covers the sealed container is provided outside the sealed container of the cool / warm compressor.   The vending machine according to any one of claims 1 to 11, wherein R600a is enclosed as a refrigerant in a cooling cycle for cooling.   The vending machine according to any one of claims 1 to 12, wherein the pressure in the sealed container of the cooling compressor and the cooling / warming compressor is a low pressure type.

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