JPH094933A - Refrigerator with deep freezer - Google Patents

Abstract

PURPOSE: To improve the starting characteristics of a refrigerator without deteriorating the reliability of a refrigerating cycle by lowering the refrigerant channel resistance in the refrigerating cycle during stopping rather than in the operation of a reciprocating compressor for compressing refrigerant. CONSTITUTION: A bypass pipe 17 is connected between two capillary tubes 14 and 15 to bypass the tube 14 at the one and the other ends of a switching valve 16. The valve 16 is so controlled as to pass refrigerant to the pipe 17 during stopping of a compressor 11 to shorten the total length of the tubes 14, 15 as compared with that during operating of the compressor 11 by a controller 18 to lower the refrigerant channel resistance in a refrigerating cycle. Thus, the flow of the refrigerant in the cycle is improved to shorten the equilibrium time of the high and low pressure of the compressor 1, and the starting characteristics of a refrigerator can be improved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerating refrigerator which uses a reciprocating compressor as a compressor and uses a capillary tube as an expansion device to improve the starting performance of the compressor without changing the specifications of the compressor.

[0002]

2. Description of the Related Art FIG. 15 shows a refrigerating cycle diagram of a general conventional refrigerator-freezer. In FIG. 15, 1 is a reciprocating compressor, 2 is a condenser, 3 is an evaporator, 4 is a dryer, and 5
Is a capillary tube which is a throttle device, that is, a pressure reducing device, and 6 is a suction pipe of a suction pipe. Also,
Reference numeral 7 is an internal cooling fan motor for heat exchange of the evaporator 3, and 8 is a condensing fan motor attached to promote heat dissipation of the condenser 2.

FIG. 16 shows the normal cooling operation, that is, the compressor 1.
The operation of the internal cooling fan motor 7 and the condensing fan motor 8 during operation and while the compressor 1 is stopped is shown. As shown in Figure 16,
The internal cooling fan motor 7 and the condenser fan motor 8 are controlled so as to be synchronized with the operation mode of the compressor 1.

It is known that such control has an adverse effect on the amount of power consumption when the internal cooling fan motor 7 is operated while the compressor 1 is stopped.
This is because the condenser 2 does not need to radiate heat during the stop.

FIG. 17 shows changes with time in the pressures inside the condenser 2 and the evaporator 3 during the operation of the compressor 1 and during the stoppage of the compressor 1. The pressure in the condenser 2 during the operation of the compressor 1 is high and near the outlet of the condenser 2, that is, the capillary tube 5
It is a liquid refrigerant at the inlet. Further, the pressure of the evaporator 3 is low during the operation of the compressor 1 and is designed so as to become a gas refrigerant near the outlet of the evaporator 3.

FIG. 18 is a simplified explanatory view of a cylinder portion of a reciprocating compressor. In the reciprocating compressor, even if the compressor 1 is stopped, since the valve 1b is present in the compressor cylinder portion 1a, the high pressure and low pressure equilibrium action does not work on the refrigerant in the path passing through the compressor 1. Therefore, the capillary tube 5
The high- and low-pressure equilibrium is performed on the refrigerant only through the path passing through.

While the compressor 1 is stopped, the compressor cylinder portion 1a
The valve 1b of Fig. 17 is under back pressure as shown in Fig. 17, and whether or not the compressor can be started at the time of restart is determined by the cylinder portion 1a.
It depends on the relationship between the high-low pressure difference and the starting torque of the compressor motor.

That is, if the starting torque of the compressor motor is the same, the startability is determined by the balance of high pressure and low pressure after the compressor 1 is stopped until it is restarted.

[0009] In recent years, the fan-type cooling is mainly used in the freezer-refrigerator, and in the fan-type refrigerator-freezer, it is necessary to defrost the evaporator in a constant operation time period.

In this type of refrigerator, the evaporator is designed to be heated by a large-capacity heater during defrosting so that the frost on the evaporator is melted. Therefore, after the completion of defrosting, the evaporator temperature becomes about + 20 ° C., and the pressure in the refrigeration cycle is balanced to a high pressure on both the high pressure side and the low pressure side. That is, when the compressor 1 is restarted after the defrosting is finished, a high back pressure is applied to the cylinder portion, and the condition for starting is a severe condition.

Further, since the evaporator temperature is high, the refrigerant having a very large specific gravity is compressed immediately after the start even if the start is successful. That is, it is necessary for the compressor motor to do a great deal of work, and a high starting torque is required.

As described above, the startability after the completion of defrosting is also determined by the relationship between the high and low pressure difference in the cylinder portion and the starting torque of the compressor motor. After the compressor is stopped, the high-low pressure equilibrium speed can be determined by the difference between the degree of narrowing of the capillary tube 5 and the high-low pressure pressure before the compressor 1 is stopped.

The narrowing degree of the capillary tube 5 and the pressure difference between the high pressure and the low pressure before the compressor 1 is stopped, that is, during the operation of the compressor 1 are designed to obtain a predetermined cooling capacity.

In recent years, HFC134a has come to be used as a refrigerant, and in a refrigeration cycle using HFC134a, in order to obtain a predetermined high / low pressure difference, the capillary tube 5 has a narrowing degree of CFC12 which is a conventional refrigerant. It is necessary to squeeze the aperture than 5
The high-low pressure equilibrium speed after the compressor 1 is stopped becomes slower, and the condition for starting becomes more severe than in the conventional CFC 12 refrigeration cycle.

Therefore, conventionally, in order to increase the speed of equilibrium of high and low pressure in the compressor cylinder part, the capillary tube 5 is used.
In many cases, the startability as a refrigerator was improved by taking measures to loosen the throttle degree or increasing the starting torque of the compressor motor.

[0016]

However, loosening the degree of narrowing of the capillary tube 5 makes it impossible to obtain a predetermined high and low pressure difference, which deteriorates the cooling capacity. Since the balance gas operation is performed under a large pressure condition, the discharge gas temperature rises, which may lead to deterioration of the reliability of the compressor and thus the refrigeration cycle. In addition, increasing the starting torque of the compressor motor increases the input of the compressor motor during normal operation, that is, reduces efficiency, leading to a large increase in power consumption.

As for the refrigerating cycle of the refrigerator, a technique has been proposed in which two evaporators are provided and a bypass passage for bypassing one evaporator and the expansion device is provided (actual exploitation 62).
No. 156767). However, in this technique, since the bypass passage having a larger flow passage resistance than that of the expansion device is provided in order to improve the cooling performance of the other evaporator, the high-low pressure equilibrium speed of the compression cylinder is not increased. However, the startability of the compressor motor cannot be improved.

The present invention has been made to solve the above-mentioned conventional problems, and it is an object of the present invention to provide a freezer-refrigerator capable of improving the startability as a refrigerator without deteriorating the reliability of the refrigerating cycle. To do.

[0019]

In order to solve the above-mentioned problems, the present invention has the following constitution. The invention of claim 1 uses a reciprocating compressor for compressing a refrigerant, a condenser for liquefying a gas refrigerant, a capillary tube for squeezing a refrigerant, and an evaporator for gasifying a liquid refrigerant, each of which is a pipe. A refrigerating refrigerator having a refrigerating cycle configured to be connected includes a flow channel resistance lowering unit that lowers a refrigerant flow channel resistance in the refrigerating cycle when the compressor is stopped rather than during operation. Have a configuration.

According to the second aspect of the invention, the flow path resistance lowering means includes a conduit having a flow resistance smaller than that of the capillary tube, and means for bypassing the capillary tube while the compressor is stopped in the conduit. It has the structure of the refrigerator-freezer according to claim 1.

In a third aspect of the invention, the flow path resistance lowering means is a condenser, a capillary tube, an evaporator, or
The refrigerating-refrigerating machine according to claim 1, wherein at least one of the suction pipes is provided with a means for controlling the temperature so as to reduce the refrigerant flow path resistance during the stop of the compressor rather than during the compressor.

According to the invention of claim 4, the means for controlling the temperature of the condenser cools the condenser after a lapse of a fixed time after stopping the compressor.

The invention of claim 5 uses a reciprocating compressor for compressing a refrigerant, a condenser for liquefying a gas refrigerant, a capillary tube for squeezing a refrigerant, and an evaporator for gasifying a liquid refrigerant, respectively. In a refrigerator-freezer having a refrigeration cycle configured by connecting the pipes with each other, there is provided a refrigerator-freezer configuration characterized in that it has means for extending a connection time of a starting capacitor of a compressor motor.

The invention of claim 6 uses a reciprocating compressor for compressing a refrigerant, a condenser for liquefying a gas refrigerant, a capillary tube for squeezing the refrigerant, and an evaporator for gasifying a liquid refrigerant, respectively. In a refrigerating refrigerator having a refrigeration cycle configured by connecting pipes with each other, means for defrosting an evaporator in the refrigeration cycle, and means for cooling the evaporator after defrosting the evaporator and before starting the compressor. It has the structure of the refrigerator-freezer characterized by having.

The invention of claim 7 uses a reciprocating compressor for compressing a refrigerant, a condenser for liquefying a gas refrigerant, a capillary tube for squeezing the refrigerant, and an evaporator for gasifying the liquid refrigerant, respectively. In a freezer-refrigerator having a refrigeration cycle configured by connecting with a pipe, an internal cooling fan motor for evaporator heat exchange in the refrigeration cycle, means for defrosting the evaporator, and after defrosting the evaporator And a means for stopping the operation of the cooling fan motor for a certain period of time after the compressor is restarted.

[0026]

According to the first aspect of the present invention, the refrigerator-freezer having the refrigeration cycle has the flow passage resistance lowering means for lowering the refrigerant flow passage resistance in the refrigeration cycle when the compressor is stopped rather than during operation. The refrigerant flow in the refrigeration cycle becomes good while the compressor is stopped, and the high-low pressure equilibration time of the compressor can be shortened.

According to a second aspect of the present invention, the flow passage resistance lowering means includes a pipe having a flow passage resistance smaller than that of the capillary tube, and a means for bypassing the capillary tube while the compressor is stopped in the pipe. You can

In claim 2, for example, a plurality of capillary tubes connected in series in the refrigeration cycle,
A bypass conduit that bypasses at least one of the plurality of capillary tubes and has a smaller flow resistance (the same as the flow resistance) than the capillary tube that bypasses, and one of the bypass conduit or the capillary tube where the refrigerant is A switching valve that changes the total length of the capillary tube by switching so that the refrigerant flows, and the total length of the capillary tube by controlling the switching valve so that the refrigerant passes through the bypass line while the compressor is stopped. With a control device that makes the length shorter than that during compressor operation.

According to the above, when the compressor is stopped,
By controlling the switching valve, the total length of the capillary tube becomes shorter than that during normal operation, and the capillary tube with a looser degree of contraction serves as the refrigerant flow path, that is, the flow path for pressure averaging, and thus the compressor The high-low pressure equilibrium speed of the refrigerant after the shutdown is increased.

Further, in claim 2, for example, a bypass pipe that bypasses the inlet side of the capillary tube and the evaporator outlet side and has a flow passage resistance smaller than that of the capillary tube, and the refrigerant is the bypass pipe or the capillary tube. It is possible to have a switching valve that switches so as to flow to one of the two, and a control device that controls the switching valve so that the refrigerant flows through the bypass line while the compressor is stopped.

In this way, by switching the refrigerant circuit from the capillary tube to the bypass line by the switching valve while the compressor is stopped, the capillary tube and the evaporator are removed from the refrigerant pressure balance path, and the compressor is removed. The high-low pressure equilibrium speed after the stop is increased.

According to the third aspect of the present invention, the flow passage resistance lowering means is provided in at least one of the condenser, the capillary tube, the evaporator, and the suction pipe so that the flow passage resistance of the refrigerant is higher than that during operation of the compressor. Also has a means to control the temperature so that it decreases during stoppage, so during this stoppage, the flow path resistance (flow rate resistance) becomes smaller than during operation, so the flow of refrigerant becomes faster and the pressure equilibration time increases. It is shortened.

In the third aspect, the flow resistance of the capillary tube is reduced by cooling the capillary tube by a cooling unit such as an electronic cooling device while the compressor is stopped. Further, for example, conversely, during normal compressor operation, the flow resistance of the capillary tube is increased by heating the capillary tube with the heater unit to a predetermined throttling degree, and the heater is turned off while the compressor is stopped to turn off the capillary tube. Reduce flow resistance. Therefore, in any case, the speed of high-low pressure equilibrium after the compressor is stopped is increased, so that even if the starting torque of the compressor is the same, there is no effect during normal compressor operation and the startability as a refrigerator is improved. Is improved.

According to the fourth aspect of the present invention, even if the compressor is stopped, if a certain time elapses, the condenser is cooled by, for example, a condenser fan motor or an electronic cooling device, so that the high pressure side when the compressor is restarted. Reduce the pressure to reduce the back pressure in the compressor cylinder. Since the equilibrium speed of pressure is higher as the pressure difference immediately after the compressor is stopped is larger, the condenser is cooled after a certain time has passed since the compressor was stopped. Therefore, even if the starting torque of the compressor is the same, the startability as a refrigerator is improved without any influence during normal compressor operation.

According to a third aspect of the present invention, for example, the suction duct of the condenser fan motor installed so as to cool the condenser during the normal operation of the compressor, and the outside air which directly sucks the outside air while the compressor is stopped, are enclosed. The temperature of the compressor motor winding can be lowered and the motor torque at the time of restarting the compressor can be increased by adopting the suction duct path leading to.

Further, in the invention of claim 3, by heating the suction pipe by the heater portion while the compressor is stopped, the pressure rise on the low pressure side after the compressor is stopped is accelerated, and by extension, the high and low pressure after the pressure is stopped. Increase the speed of equilibration. As a result, even if the starting torque of the compressor is the same, there is no effect during normal compressor operation, and the startability as a refrigerator is improved.

According to the invention of claim 5, since the connection time of the starting capacitor of the compressor motor is extended, a sufficient starting torque can be obtained from the compressor motor at the time of restart of the compressor which has a high pressure and is difficult to start. .

For example, while the compressor is stopped, the PTC relay for starting the compressor is cooled by the cooling unit such as the electronic cooling device, and instead of the PTC relay, the controller for controlling the compressor is used for starting the compressor. The setting of the energization time to the circuit via the starting capacitor is lengthened to increase the motor torque when the compressor is restarted. As a result, even if the specifications of the compressor are the same, the starting torque at the time of restart is increased, and the startability as a refrigerator is improved.

According to the sixth aspect of the invention, if the evaporator is cooled after defrosting the evaporator and before starting the compressor, the evaporator temperature after defrosting is lowered, that is, the pressure in the cycle is lowered, and The specific gravity of the sucked refrigerant after starting is reduced to reduce the load on the compressor. The evaporator temperature can be lowered by operating a cooling fan motor or by an electronic cooling device.

According to the invention of claim 7, after the evaporator is defrosted and the compressor is started, the internal cooling fan motor is stopped for a certain period of time to lower the evaporator temperature immediately after the restart and to restart the evaporator. The specific gravity of the suctioned refrigerant is reduced to reduce the load on the compressor. As a result, even if the starting torque of the compressor is the same, the startability of the refrigerator after defrosting is improved.

[0041]

Embodiments of the present invention will be described below in detail with reference to the drawings. (First Embodiment) As shown in FIG. 1, a refrigerator-freezer according to a first embodiment of the present invention includes a reciprocating compressor 11 as a compressor for compressing a refrigerant, a condenser 12 for liquefying a gas refrigerant, and a liquid. An evaporator 13 for gasifying the refrigerant, a first capillary tube 14 and a second capillary tube 15 which are throttle devices (that is, pressure reducing devices) connected in series, respectively.
A switching valve 16 located on the inlet side of the first capillary tube 14 and switched so that the refrigerant flows into one of the bypass pipe line 17 and the first capillary tube 14 to make the total length of the capillary tube variable. A bypass pipe 17 having one end connected to the switching valve 16 and the other end connected between the two capillary tubes 14 and 15 to bypass the first capillary tube 14; A control device 18 is provided to control the switching valve 16 so that the refrigerant passes through the bypass pipe 17 so that the total length of the capillary tubes 14 and 15 is shorter than that during the operation of the compressor 11.

The bypass pipe 17 has a narrowing degree smaller than that of the first capillary tube 14 and has a small flow resistance. Further, in FIG. 1, reference numeral 19a is a dryer and 1
9b is a condensing fan motor for promoting heat dissipation from the condenser 12, and 19c is an internal fan motor for exchanging heat with the evaporator 13.

In the above structure, the first capillary tube 1 is set as the predetermined throttle ratio during the normal operation of the compressor 11.
4 and the second capillary tube 15 are set as the total aperture.

The refrigerant condensed in the condenser 12 circulates in the cycle using the first capillary tube 14 and the second capillary tube 15 as flow paths. Here, when the internal temperature reaches the set temperature and the compressor 11 stops, the control device 1
The switching valve 16 operates by 8, and the first capillary tube 14 is bypassed by the bypass pipe 17, so that only the second capillary tube 15 serves as a refrigerant flow path. That is, the total length of the capillary tubes through which the refrigerant passes becomes short, the flow resistance becomes low, and the high-low pressure equilibrium speed of the refrigerant after the compressor 11 is stopped becomes fast. As a result, even if the starting torque of the compressor 11 is the same, there is no effect during normal operation of the compressor 11 and the starting performance as a refrigerator is improved.

(Second Embodiment) A freezer-refrigerator according to a second embodiment of the present invention is used as a compressor for compressing a refrigerant as shown in FIG.
A reciprocating compressor 21, a condenser 22 that liquefies the gas refrigerant, an evaporator 23 that gasifies the liquid refrigerant, a capillary tube 24 of the expansion device, and a refrigerant from the inlet side of the capillary tube 24 to the outlet side of the evaporator 23. A bypass pipe 25 that bypasses the circuit, and a refrigerant that is attached near the inlet of the capillary tube 24 and has a refrigerant
5 or one of the capillary tubes 24, and a switching valve 26 for switching the refrigerant to flow to the bypass pipe 25 while the compressor 21 is stopped.
A control device 27 for controlling the control unit 6 is provided. In addition,
In FIG. 2, 28 is a dryer.

In the above structure, when the internal temperature reaches a predetermined temperature and the compressor 21 is stopped, the switching valve 26 is operated by the control device 27, and the refrigerant evaporates from the inlet side of the capillary tube 24 using the bypass pipe 25 as a flow path. The refrigerant circuit to the outlet side of the container 23 is bypassed. Since the inner diameter of the bypass pipe 25 is larger than that of the capillary tube 24, the flow resistance is small (the degree of throttling is small), and the high-low pressure equilibrium speed after the compressor 21 is stopped is significantly increased. As a result, even if the starting torque of the compressor 21 is the same, the normal compressor 2
1. There is no effect during operation, and the startability as a refrigerator is improved.

In the second embodiment, the refrigerant gasified in the condenser 22 when the compressor 21 is stopped (during stop) is the evaporator 2.
3 will no longer flow into the compressor, dissipate heat and condense.
1 Heat loss during stoppage is prevented and there is also an effect of reducing power consumption.

(Third Embodiment) A freezer-refrigerator according to a third embodiment of the present invention is, as shown in FIG. 3, a reciprocating compressor 31 as a compressor for compressing a refrigerant and a condenser 32 for liquefying a gas refrigerant. A refrigeration cycle having an evaporator 33 for gasifying the liquid refrigerant, and a capillary tube 34 of an expansion device, and an electronic cooling device 35 attached so as to cool the capillary tube 34, and an electronic cooling device. 35 is turned on while the compressor 31 is stopped, and the compressor 3
1 and a control device 36 that is turned off during operation. In FIG. 3, reference numeral 37a denotes a dryer, 37
Reference numeral b is a condensing fan motor for promoting heat dissipation of the condenser 32, and 37c is an internal fan motor for heat exchange of the evaporator 33.

In the above structure, during the normal operation of the compressor 31, the refrigerant condensed in the condenser 32 uses the capillary tube 31 which is set so as to obtain a predetermined throttling degree, that is, a predetermined pressure difference, as a flow path. Circulate in the refrigeration cycle. When the internal temperature reaches the set temperature and the compressor 31 stops, the controller 36 operates the electronic cooling device 35 to cool the capillary tube 35. As a characteristic of the refrigerant, as the temperature of the capillary tube 35 decreases, the flow resistance decreases, and the high-low pressure equilibrium speed after the compressor 31 stops becomes faster.

As a result, even if the starting torque of the compressor 31 is the same, there is no effect during normal operation of the compressor 31, and the starting performance is improved without changing the specifications of the refrigerator.

(Fourth Embodiment) As shown in FIG. 4, a refrigerator-freezer according to a fourth embodiment of the present invention serves as a compressor for compressing a refrigerant.
The reciprocating compressor 41, the condenser 42 for liquefying the gas refrigerant, the evaporator 43 for gasifying the liquid refrigerant, the capillary tube 44 of the expansion device, and the capillary tube 44 are attached so as to heat the vicinity of the inlet. The heater 45 and the heater 45 are turned off while the compressor 42 is stopped,
A control device 46 that is turned on while the compressor 42 is operating is provided. In FIG. 4, reference numeral 47a is a dryer, 47b is a condensing fan motor for promoting heat dissipation of the condenser 42, and 47c is an internal fan motor for heat exchange of the evaporator 43.

In the above-mentioned structure, the drawing degree of the capillary tube 44 is set to be loose with respect to a predetermined drawing degree. During the normal operation of the compressor 42, the control device 46
The heater is turned on to heat the vicinity of the inlet of the capillary tube 44. As a characteristic of the refrigerant, if the temperature of the capillary tube 44 rises, the flow resistance increases, and the degree of throttling of the capillary tube 44 becomes a predetermined degree of throttling, and operation is performed in balance with a predetermined pressure difference.

When the internal temperature reaches the set temperature and the compressor 41 is stopped, the heater 45 is turned off by the control device 46, the capillary tube 44 is not heated, the flow resistance is reduced, and the high temperature after the compressor 41 is stopped. The low-pressure equilibrium speed increases.

As a result, even if the starting torque of the compressor 41 is the same, there is no effect during normal operation of the compressor 41, and the startability as a refrigerator is improved at a relatively low cost.

(Fifth Embodiment) A freezer-refrigerator according to a fifth embodiment of the present invention is used as a compressor for compressing a refrigerant as shown in FIG.
A reciprocating compressor 51, a condenser 52 for liquefying a gas refrigerant, an evaporator 53 for gasifying a liquid refrigerant, a capillary tube 54 of an expansion device, and a condensing fan attached to cool the condenser 52. When the motor 55 and the compressor 51 are stopped, the condensing fan motor 55 is stopped, and when a certain time elapses after the compressor 51 is stopped, the compressor 5
A control device 56 that operates the fan motor 55 even in the stop state of No. 1 is provided. Reference numeral 57a is a dryer and 57b is an internal fan motor.

In the above structure, when the internal temperature reaches the set temperature and the compressor 51 stops, the controller 56 stops the condenser fan motor 55. The liquid refrigerant in the condenser 53 is gasified and flows into the evaporator 53, so that the pressure in the refrigeration cycle begins to equilibrate. The greater the pressure difference immediately after the compressor 51 is stopped, the faster the pressure equilibrium speed is.
By stopping the condensing fan motor 55, the initial pressure equilibration speed becomes faster.

When the pressure equilibrates to some extent with the passage of time, the pressure equilibration speed becomes slow. At this point, by operating the condenser fan motor 55, the temperature of the condenser 53 is lowered and the pressure itself in the refrigeration cycle is lowered. That is, the pressure in the refrigeration cycle before starting the compressor 51 decreases. As a result, even if the starting torque of the compressor 51 is the same, the startability as a refrigerator is improved without affecting during the normal operation of the compressor 51. Moreover, there is no need to add new parts, which is simple and inexpensive.

(Sixth Embodiment) A freezer-refrigerator according to a sixth embodiment of the present invention is used as a compressor for compressing a refrigerant as shown in FIG.
Reciprocating compressor 61, condenser 62 for liquefying the gas refrigerant, and evaporator (not shown) for gasifying the liquid refrigerant.
A condenser tube (not shown) of the expansion device and a condensing fan motor 65 mounted to cool the condenser 62, and a suction duct path of the condensing fan motor 65 sucks the outside air and discharges it toward the compressor 61. There is provided a movable suction duct 66 having a mechanism capable of being variable in the path, and a control device 67 for directing the suction duct path to the compressor 61 while the movable suction duct 66 is stopped. Reference numeral 68 is a suction duct during operation of the compressor 61.

In the above structure, the movable suction duct 66 has a duct path so as to cool the condenser 61 during the normal operation of the compressor 61. When the internal temperature reaches the set temperature and the compressor 61 is stopped, the condensing fan motor 65 operates as it is, but the control suction device 67 causes the movable suction duct 66 to suck the outside air, and the compressor 6 is operated.
1 Switch to the route of exhalation toward the outer contour. As a result, the winding temperature of the compressor 61 motor before the compressor 61 is restarted is reduced, and even if the compressor has the same specification, the input does not increase during normal compressor operation. The starting torque is increased without changing the specifications of the compressor, and the starting performance as a refrigerator is improved.

(Seventh Embodiment) A refrigerator-freezer according to a seventh embodiment of the present invention cools the condenser 72 as shown in FIG. 7 in the same manner as in the fifth embodiment (FIG. 5). Instead of controlling 55, the electronic cooling device 73 is used. The operation of the electronic cooling device 73 is the same as the cooling operation of the condensing fan motor 55 of the fifth embodiment (FIG. 5) and is performed by the control device 74, but the description thereof is omitted. Further, in the other components, the same parts as those in the fifth embodiment (FIG. 5) are designated by the same reference numerals and the description thereof will be omitted. In addition, during normal operation,
The condenser fan motor 55 blows air to the condenser 72, and the fan motor 55 is stopped during the stop. Further, since the electronic cooling device is finely operated and only needs to be operated when necessary, it consumes less energy.

(Eighth Embodiment) A freezer-refrigerator according to an eighth embodiment of the present invention is, as a compressor for compressing a refrigerant, as shown in FIG.
It has a reciprocating compressor, a condenser that liquefies the gas refrigerant, an evaporator that gasifies the liquid refrigerant, and a capillary tube of the expansion device (these are the same as those in the other embodiments described above, so illustration is omitted). The electronic cooling device 86 installed so as to cool the PTC relay 85 for starting the compressor motor 81m and the control device 87 that turns on the electronic cooling device 86 while the compressor is stopped are provided.

Normally, the PTC relay 85 is connected to a circuit via a starting capacitor 85a which increases the motor torque only at the time of starting which requires a large motor torque.
It is configured to switch to a circuit (capacitor 85c or the like) that does not include the starting capacitor 85a after a certain period of time due to the temperature rise of the element 85b inside the relay. In addition,
Reference numeral 88a is a power supply, and 88b is a power supply switch of the compressor motor 81m.

In the above configuration, when the internal temperature reaches the set temperature and the compressor is stopped, the electronic cooling device 86 is turned on by the control device 87 and the PTC relay 8 for starting the compressor 8
5 is cooled. As a result, P when the compressor is restarted
Since the temperature of the TC relay 85 is low, the time for energizing the circuit via the starting capacitor 85b for starting the compressor at the time of starting becomes long, and even if the specifications of the compressor 81m and the PTC relay 85b of the same specification are started, The torque is increased and the startability as a refrigerator is improved.

(Ninth Embodiment) As shown in FIG. 9, the refrigerator-freezer of the ninth embodiment of the present invention is controlled in place of the PTC relay 85 for starting the compressor motor 81m of the eighth embodiment (FIG. 8). A control device 91 is provided which is connected to the switch 92 and is capable of controlling the on / off of the control switch 92 to set the energization time of the circuit for adding (connecting) the starting capacitor 85a for starting the compressor. . Others are the same as those in the eighth embodiment (FIG. 8), and therefore, the same reference numerals are given and the description is omitted.

In the above structure, when the compressor is restarted, the control device 91 forms a circuit for adding (connecting) the starting capacitor 85a to the compressor motor 81m for a time period required for a large starting torque.

As in the eighth embodiment, the PTC relay 85
In the case of a circuit using, there is a method of increasing the resistance of the PTC relay internal element 85b and slowing the temperature rise in order to increase the energization time to the circuit to which the starting capacitor 85a is added.
Increasing the resistance of the internal element 85b is performed by the compressor motor 81.
It also has the effect of reducing the inrush current to m and the starting torque.

The eighth and ninth embodiments have the effect of lengthening the high starting torque time without lowering the starting torque. Even if the compressor specifications are the same, the starting performance as a refrigerator is improved. .

(Tenth Embodiment) A refrigerator-freezer according to a tenth embodiment of the present invention is, as shown in FIG. 10, a reciprocating compressor 101 as a compressor for compressing a refrigerant and a condenser 102 for liquefying a gas refrigerant. And an evaporator 10 for gasifying the liquid refrigerant
3, the capillary tube 104 of the expansion device, the compressor 101, and the suction pipe 105 that is the suction side pipe.
The heater 106 attached to heat the compressor 10 and the heater 106 is turned on while the compressor 101 is stopped,
A control device 107 that is turned off during the operation of No. 1 is provided. Reference numeral 108 is a dryer.

In the above structure, the heater 106 is turned off by the control device 107 during the normal operation of the compressor 101. When the internal temperature reaches the set temperature and the compressor 101 is stopped, the heater 106 is turned on by the control device 107 to heat the suction pipe 105, and the rising speed of the low pressure side pressure in the refrigeration cycle increases. That is, the high-low pressure equilibrium speed after the compressor 101 is stopped is increased. As a result, even if the starting torque of the compressor 101 is the same, there is no effect during normal operation of the compressor 101, and the startability as a refrigerator is improved.

(Eleventh Embodiment) As shown in FIG. 11, a freezer-refrigerator according to an eleventh embodiment of the present invention has a reciprocating compressor 111 as a compressor for compressing a refrigerant and a condenser 112 for liquefying a gas refrigerant. And an evaporator 11 for gasifying the liquid refrigerant
3, the internal fan motor (internal cold fan motor) 115 for heat exchange of the evaporator 113, the capillary tube 114 of the expansion device, and the internal fan motor 115 after the defrosting of the evaporator 113 is completed, the compressor A control device 116 that operates for a certain period of time before the start of 111 is provided. In addition,
In FIG. 11, reference numeral 117a is a dryer, 117b condensing fan motor.

Further, FIG. 12 shows a compressor 111 and an evaporator 1.
13 is an energization time chart for the defrosting heater 13 and the internal fan motor 115. Generally, a time-safe of 3 to 5 minutes is provided after the defrosting of the evaporator 113 is completed and before the compressor 111 is restarted.

In the eleventh embodiment, in the above structure, the controller fan drives the internal fan motor 115 during the time-safe after the defrosting of the evaporator 113 is completed and before the compressor 111 is restarted.

By operating the internal fan motor 115, the evaporator 113 can be air-cooled to lower its temperature, that is, the internal pressure of the cycle can be lowered, and the specific gravity of the sucked refrigerant after starting can be lowered to reduce the load on the compressor. it can. As a result, even if the starting torque of the compressor 111 is the same, the startability of the refrigerator after defrosting is improved. Here, since the evaporator side was heated after defrosting, the pressure on the evaporator side (low pressure side) is high, and if it is restarted, the specific gravity of the suction refrigerant will increase and In general, the compressor is placed in a start waiting state for a certain time (time safe 3 to 5 minutes) after the defrosting is completed because the load becomes heavy and the engine cannot be started. During this time-safe period (3 to 5 minutes), the pressure on the evaporator side drops by about 0.5 to ¹ kgf / cm ² ,
Easy to start. In the eleventh embodiment, the cooling fan motor is operated during this time-safe to forcibly cool the evaporator to reduce the pressure, and the pressure is 2-3 kgf / c.
The pressure can be lowered by about m ² , and the startability is remarkably improved.

(Twelfth Embodiment) A component group of a refrigerator / freezer according to a twelfth embodiment of the present invention is the same as the eleventh embodiment (FIG. 1).
Same as 1). Further, FIG. 13 shows a compressor 111, a defrosting heater for the evaporator 113, and an internal fan motor 115.
FIG. Generally, the evaporator 113
After the defrosting is completed, it takes 3 minutes to restart the compressor 111.
There is a 5 minute time safe.

In the twelfth embodiment, in the above configuration, the compressor 111 is restarted after the defrosting of the evaporator 113 is finished, in a time-safe manner. However, a few minutes after the restart of the compressor 111, The internal fan motor 1 is controlled by the controller 116.
15 remains stopped. Stopping the internal fan motor 115 significantly reduces the amount of heat exchange in the evaporator 113,
The temperature of the evaporator 113 is lowered, that is, the specific gravity of the suctioned refrigerant after starting can be lowered and the load on the compressor can be reduced. As a result, even if the starting torque of the compressor is the same, the startability of the refrigerator after defrosting is improved. In the twelfth embodiment, the pressure reduction measure is not forcibly performed during the time safe, but the cooling fan is not operated for about 1 minute immediately after restarting. Since the amount of heat exchange of (1) is remarkably reduced, the suction specific gravity of the compressor is reduced, the load is reduced, and the startability is improved. The degree of improvement in startability is greater in the eleventh embodiment, but in the eleventh embodiment, after defrosting, air in the cooling chamber heated to about 20 ° C. is discharged to the freezing chamber. Depending on the situation, the temperature of food may rise. Therefore, the twelfth embodiment is intended to improve the startability after defrosting of the product in which the eleventh embodiment cannot be used.

(Thirteenth Embodiment) A freezer-refrigerator according to a thirteenth embodiment of the present invention is, as shown in FIG. 14, a reciprocating compressor 141 as a compressor for compressing a refrigerant and a condenser 142 for liquefying a gas refrigerant. And an evaporator 14 for gasifying the liquid refrigerant
3, the capillary tube 144 of the expansion device, and the electronic cooling device 1 attached so as to cool the evaporator 143.
45 and a control device 146 of the electronic cooling device are provided. Reference numeral 147a is a dryer and 147b is a condenser fan motor.

In the above structure, after the defrosting of the evaporator 143 is completed, during the time-safe until the compressor 141 is restarted,
The electronic cooling device 145 is energized by the control device 146.

By the electronic cooling device 145, the evaporator 14 is
3 is cooled, the temperature of the evaporator 143 is lowered, that is, the internal pressure of the cycle is lowered, and the specific gravity of the sucked refrigerant after the start is lowered to reduce the load on the compressor 141. With these, even if the starting torque of the compressor 141 is the same, the startability after defrosting as the refrigerator is improved. Further, it is possible to suppress the temperature rise that does not come after defrosting.

[0079]

As is apparent from the above description, the present invention has the following effects. According to the invention of claim 1, the flow of the refrigerant is improved in the refrigeration cycle while the compressor is stopped, and the high-low pressure equilibration time of the compressor can be shortened.

According to the second aspect of the present invention, the pressure equilibrium speed in the refrigeration cycle is increased by, for example, changing the length of the capillary tube through which the refrigerant passes by the switching valve when the compressor is stopped. Further, for example, by bypassing the circuit on the evaporator side from the capillary tube with a switching valve when the compressor is stopped, the pressure equilibrium speed in the refrigeration cycle can be increased, and startability can be improved without changing the specifications of the compressor. , It is effective in preventing heat loss in the evaporator when the compressor is stopped.

According to the third aspect of the present invention, at least one of the condenser, the capillary tube, the evaporator, and the suction pipe is controlled so that the refrigerant flow path resistance is reduced during the stoppage of the compressor rather than during the operation of the compressor. Because it is controlled, the capillary tube is cooled when the compressor is stopped, and the flow rate resistance (flow path resistance) of the refrigerant flowing through the capillary tube is reduced, thereby increasing the pressure equilibration speed in the refrigeration cycle and changing the compressor specifications. The startability can be improved.

For example, conversely, the capillary tube is heated when the compressor is in operation, and the heating is stopped when the compressor is stopped to reduce the flow resistance of the refrigerant flowing through the capillary tube, thereby increasing the pressure equilibrium speed in the refrigeration cycle. The startability can be improved relatively inexpensively without changing the specifications of the compressor.

In a fourth aspect of the present invention, when a certain period of time elapses after the compressor is stopped, the specifications of the compressor are changed by cooling the condenser and reducing the internal pressure of the condenser by, for example, a condenser fan motor or an electronic cooling device. The startability can be improved without Further, since the startability can be improved by using the existing condensing fan motor, it is not necessary to add new parts, and it is simple and inexpensive.

According to the fifth aspect of the present invention, since the connection time of the starting capacitor of the compressor motor is extended, a sufficient starting torque can be obtained from the compressor motor at the time of restart of the compressor having a high pressure and difficult to start. .

According to the sixth aspect of the present invention, by operating the cooling fan motor after defrosting the evaporator and before starting the compressor,
The startability after defrosting is improved without changing the specifications of the compressor.

According to the seventh aspect of the present invention, after the evaporator is defrosted and the compressor is started, the cooling fan motor is temporarily stopped to improve the startability after defrosting without changing the specifications of the compressor. At the same time, the generation of refrigerant flow noise in the evaporator after defrosting can be suppressed.

[Brief description of drawings]

FIG. 1 is an explanatory diagram of a refrigeration cycle according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram of a refrigerating cycle according to a second embodiment of the present invention.

FIG. 3 is an explanatory diagram of a refrigerating cycle according to a third embodiment of the present invention.

FIG. 4 is an explanatory diagram of a refrigerating cycle according to a fourth embodiment of the present invention.

FIG. 5 is an explanatory diagram of a refrigerating cycle according to a fifth embodiment of the present invention.

FIG. 6 is an explanatory diagram of a refrigerating cycle according to a sixth embodiment of the present invention.

FIG. 7 is an explanatory diagram of a refrigeration cycle according to a seventh embodiment of the present invention.

FIG. 8 is an explanatory diagram of a refrigerating cycle according to an eighth embodiment of the present invention.

FIG. 9 is an explanatory diagram of a refrigerating cycle according to a ninth embodiment of the present invention.

FIG. 10 is an explanatory diagram of a refrigeration cycle according to a tenth embodiment of the present invention.

FIG. 11 is an explanatory diagram of a refrigeration cycle according to an eleventh embodiment of the present invention.

FIG. 12 is an explanatory diagram of an energization time chart according to an eleventh embodiment of the present invention.

FIG. 13 is an explanatory diagram of an energization time chart according to the twelfth embodiment of the present invention.

FIG. 14 is an explanatory view of a refrigerating cycle according to a 13th embodiment of the present invention.

FIG. 15 is an explanatory view of a conventional refrigeration cycle and peripheral parts.

FIG. 16 is an operation time chart explanatory diagram of a conventional compressor and parts around the compressor.

FIG. 17 is an explanatory diagram of changes in pressure over time of a conventional refrigeration cycle.

FIG. 18 is a simplified explanatory diagram of a cylinder portion of a reciprocating compressor.

[Explanation of symbols]

11-141 Compressor 12-142 Condenser 13-143 Evaporator 14-144 Capillary tube 16 Switching valve 17 Bypass pipe 18, 27, 36, 46, 56, 67, 74, 87, 9
1, 107, 116, 146 Control device 25 Bypass pipe 26 Switching valve

Claims (7)

[Claims] 1. A reciprocating compressor for compressing a refrigerant,
Using a condenser that liquefies the gas refrigerant, a capillary tube that throttles the refrigerant, and an evaporator that gasifies the liquid refrigerant,
A freezer-refrigerator having a refrigeration cycle configured by connecting each of them with a pipe, characterized by having a flow path resistance lowering means for lowering the refrigerant flow path resistance in the refrigeration cycle when the compressor is stopped rather than during operation. A freezer refrigerator. 2. The flow path resistance lowering means includes a conduit having a flow resistance smaller than that of the capillary tube, and means for bypassing the capillary tube while the compressor is stopped in the conduit. The freezer-refrigerator according to Item 1. 3. The flow path resistance lowering means reduces the flow path resistance of the refrigerant in at least one of the condenser, the capillary tube, the evaporator, and the suction pipe when the compressor is stopped rather than during operation. The refrigerator-freezer according to claim 1, further comprising a temperature control means. 4. The refrigerator-freezer according to claim 3, wherein the means for controlling the temperature of the condenser cools the condenser after a lapse of a certain time after stopping the compressor. 5. A reciprocating compressor for compressing a refrigerant,
Using a condenser that liquefies the gas refrigerant, a capillary tube that throttles the refrigerant, and an evaporator that gasifies the liquid refrigerant,
A refrigerating refrigerator having a refrigerating cycle configured by connecting each of them with a pipe, comprising a means for extending a connecting time of a starting capacitor of a compressor motor. 6. A reciprocating compressor for compressing a refrigerant,
Using a condenser that liquefies the gas refrigerant, a capillary tube that throttles the refrigerant, and an evaporator that gasifies the liquid refrigerant,
In a freezer-refrigerator having a refrigeration cycle configured by connecting them with pipes, means for defrosting an evaporator in the refrigeration cycle, and cooling the evaporator after defrosting the evaporator and before starting the compressor A freezer-refrigerator having means. 7. A reciprocating compressor for compressing a refrigerant,
Using a condenser that liquefies the gas refrigerant, a capillary tube that throttles the refrigerant, and an evaporator that gasifies the liquid refrigerant,
In a freezer-refrigerator having a refrigeration cycle configured by connecting them with pipes, an internal cooling fan motor for evaporator heat exchange in the refrigeration cycle, means for defrosting the evaporator, and removal of the evaporator A refrigerator / freezer comprising means for stopping the operation of the cooling fan motor for a certain period of time after the compressor is restarted after frost.