WO2016080788A1

WO2016080788A1 - Dryer

Info

Publication number: WO2016080788A1
Application number: PCT/KR2015/012487
Authority: WO
Inventors: 와키사카에이지; 기타무라스스무; 기타야마나오키; 시마다타츠시
Original assignee: 삼성전자주식회사
Priority date: 2014-11-19
Filing date: 2015-11-19
Publication date: 2016-05-26

Abstract

Disclosed is a heat-pump type dryer that can keep down a manufacturing cost and maintain the amount of heat discharged from an auxiliary heat exchanger at a proper level. The clothes dryer (D) comprises: a housing (1); a drum (2) that is installed in the housing (1) and receives clothes therein; a circulation-type air passage (3) that passes through the drum (2); a heat pump device (5) that has a compressor (52), a condenser (53), a throttle part (54), and an evaporator (51) that are connected to form a flow path along which a refrigerant circulates; an auxiliary heat exchanger (55) installed outside the air passage (3) and connected in series to a flow passage in the condenser (53) or in parallel to the condenser (53); and a cooling means (6) capable of cooling the auxiliary heat exchanger (55).

Description

dryer

The present invention relates to a dryer used for drying clothes.

In patent document 1, an example of a heat pump type dryer is described. This heat pump type dryer has an auxiliary heat exchanger (second condenser) connected in parallel with a condenser outside the ventilation path through which air for drying circulates. In addition, a switching valve controllable by a predetermined signal is provided at a connection portion immediately upstream of the condenser (that is, a branch portion connected to a flow passage immediately downstream of the compressor and a flow passage immediately upstream of the condenser and the auxiliary heat exchanger). Is installed. This switching valve is comprised so that the flow path which flows the refrigerant | coolant discharged | emitted from a compressor only to a condenser, the flow path which flows by dividing to a condenser and an auxiliary heat exchanger, or the flow path which flows only to an auxiliary heat exchanger can be formed. When there is a possibility that the air in the ventilation path is overheated or the refrigerant may be overheated, the dryer flows a predetermined amount of refrigerant to the auxiliary heat exchanger through control of the switching valve. The refrigerant flowing through the auxiliary heat exchanger is naturally radiated and cooled by contact with air outside the ventilation path. In the flow passage that continues from the compressor to the condenser, a refrigerant having a relatively high temperature and high pressure flows before completion of heating of the air in the air passage, so that an auxiliary heat exchanger is provided to prevent overheating and overpressure of such refrigerant, thereby operating the compressor. This prevents a situation such as a problem occurring.

Patent Document 2 discloses another example of a heat pump type dryer. This heat pump type dryer has an auxiliary heat exchanger (sub-heat exchanger) which connects directly downstream of a condenser (main heat exchanger) and immediately upstream of a throttling mechanism to the outside of a ventilation path. That is, the refrigerant passing through the condenser flows into the throttling mechanism after passing through the auxiliary heat exchanger. The refrigerant flowing through the auxiliary heat exchanger described in Patent Document 2 is forcibly radiated and cooled by blowing from a cooling fan provided outside the ventilation path. The blowing from the cooling fan cools the refrigerant pipe through which the refrigerant immediately after being discharged from the compressor flows after cooling the auxiliary heat exchanger.

In addition, the circulation type clothes dryer which circulates the air dehumidified and heated by the heat exchanger comprised as mentioned above is known conventionally. In such a circulating clothes dryer, a cooling device for cooling and dehumidifying the drying air, a heating device for heating the air passing through the cooling device, and a fan device for circulating the drying air in a circulation ventilation path are all included. It is arranged to be located in a circulation ventilation path.

In the clothes dryer, when a fan device is provided immediately downstream of the heat exchanger, it is difficult to ensure sufficient space in the thickness direction of the blowing duct provided between the fan device and the air inlet of the drum, and thus an ideal air path. Is difficult to form, and the ventilation resistance at the air inlet of the drum is increased, resulting in a pressure loss and a decrease in the amount of air for drying air. In addition, since the air for drying at the blower outlet side of the fan apparatus becomes a high pressure, there is a problem of a decrease in the amount of air due to noise or pressure loss in the circulation ventilation path. Therefore, in order to secure sufficient air volume, it is conceivable to increase the rotation speed of the fan or increase the diameter of the fan. However, problems arise in terms of noise and energy saving.

As a method of improving the flow of drying air in the case of providing a fan device immediately downstream of the heat exchanger, Patent Document 3 discloses drying air that is sent out from a jet port of a fan device (Dry Fan in Patent Document 3). An example of installation of an air guide for improving the flow of air is disclosed. In addition, Patent Literature 4 discloses a technique in which a deflection plate is provided downstream of a heater in a clothes dryer, and the deflection plate deflects the drying air introduced into the drum from the circulation duct by the deflection plate.

Moreover, it is related with the improvement of a dryer, and the technique regarding the fixing method and structure of a control board especially is also known.

For example, Patent Document 5 includes a housing having a frontal plate, a rear plate, a ceiling plate, a bottom plate, and a pair of side plates, the housing having an approximately rectangular parallelepiped shape having an opening for opening and receiving a drying object in the front plate, and the opening in the housing. Disclosed is a dryer having a bottomed cylindrical drum housed to be opened to the side, and having a control circuit unit disposed at one side plate side corner portion in a space between the drum and the ceiling plate.

In patent document 6, the circuit case which accommodated the control board is fixed to a housing so that it may be located in one side plate side corner part in the space between a drum and a ceiling plate, and a cover member is fixed to a circuit case so that the said control board may be covered. have. In addition, the wiring work between the control board and the device outside the circuit case is performed in a state where the cover member is removed.

By the way, the dryer comprised as mentioned above has a problem in various aspects, and by improving such a problem, there exists a demand to improve the performance of a dryer or to improve reliability.

As one of such problems, the dryer described in Patent Document 1 has a problem that the manufacturing cost increases only for the switching valve and the control system.

On the other hand, unlike the patent document 1, the dryer of patent document 2 does not radiate heat through control of a switching valve, but heats it through control of a cooling fan. Usually, like a cooling fan, the cooling means arrange | positioned outside a heat path apparatus separate from a heat pump apparatus is comprised more cheaply than a switching valve. Therefore, by applying the cooling fan instead of the switching valve, the manufacturing cost can be suppressed.

By the way, the inventors of the present invention have found that, when a cooling means such as a cooling fan is applied, there are the following problems, which are different from those when the switching valve is applied.

That is, when applying a switching valve, it is necessary to connect an auxiliary heat exchanger in parallel with a condenser in order to branch the flow path which continues from a compressor. On the other hand, when applying a cooling fan, since it is not necessary to branch a flow path, what is necessary is just to connect an auxiliary heat exchanger in series with a condenser.

However, in the latter case, if the auxiliary heat exchanger is provided immediately downstream of the condenser, like the dryer described in Patent Literature 2, there is a fear that the amount of heat radiation is insufficient. That is, in the structure described in Patent Literature 2, since it is not possible to directly radiate heat from a relatively high temperature and high pressure refrigerant flowing through the flow path from the compressor to the condenser, overheating and overpressure of the refrigerant are caused while the operation of the dryer is continued. Furthermore, there exists a possibility that it may interfere with the operation | movement of a compressor.

On the other hand, for example, when the auxiliary heat exchanger is installed directly upstream of the condenser, the problem of insufficient heat dissipation may be solved because the refrigerant having a relatively high temperature and high pressure can be directly cooled, but the heat dissipation from the refrigerant before passing through the condenser is solved. Therefore, depending on the amount of air blown from the cooling fan, the heat dissipation amount may be excessive, and the amount of heat required for heating the air may also be dissipated.

In solving this problem, it is conceivable to vary the blowing performance of the cooling fan in accordance with the operating conditions of the dryer. However, such a measure is not preferable because it causes an increase in manufacturing cost.

Moreover, the above-mentioned problem regarding a cooling fan is a problem common to the heat pump type dryer which provided the separate cooling means outside the ventilation path.

In view of the problems associated with

Patent Documents

1 and 2 above, in a heat pump type dryer, there is a demand to reduce the amount of heat radiation from the auxiliary heat exchanger to an appropriate amount while suppressing the production cost.

Moreover, the air guide and the deflection plate which were disclosed by

patent document

3, 4 are a technique which improves the flow of the drying air between a fan apparatus and a heater, the flow of the air which passes through the air inlet of a drum, or a fan apparatus. It is only improving in the local part of the flow of the drying air which is introduce | transduced into a drum through a blowing duct from the. In addition, the air guide and the deflection plate are separate parts, respectively, and an increase in the part cost and an increase in the manufacturing cost occur.

In view of the problems associated with

Patent Documents

3 and 4 above, the drying time is reduced in the dryer by reducing the pressure loss in the air blowing path between the fan apparatus and the air inlet port of the drum. There is a demand to make it possible to shorten, i.e., to shorten the drying time, reduce noise, and save energy at low cost.

In addition, although the schematic position of the control circuit unit is disclosed by patent document 5, there is no description regarding a specific fixing method and installation structure.

Patent Document 6 discloses a method of fixing a circuit case accommodating a control board to a housing in a state in which a cover member is removed. In this case, however, the circuit case is directly fixed to the housing. The external force applied to the control board is largely transmitted to the control board through the circuit case, which is likely to cause damage to the control board. In addition, since the circuit case is not supported from below, the force applied to the circuit case at the time of connection work or transportation may cause damage to the circuit case and the control board therein. In addition, the force applied to the circuit case during the wiring operation or transportation may cause the circuit case to come off the housing and come into contact with the rotating drum, causing damage to the circuit case and the control board therein.

In view of the problems relating to

Patent Documents

5 and 6 above, there is a demand for a dryer to prevent damage to a circuit case and a control board therein and to facilitate assembly work and maintenance inspection work from above.

This invention is made | formed in view of such a point, and the 1st objective is to improve the performance of a dryer by making the amount of heat radiation from an auxiliary heat exchanger into an appropriate amount.

A second object of the present invention is to improve the performance of the dryer by reducing the drying time, reducing the noise and saving energy at low cost.

A third object of the present invention is to improve the reliability of the dryer by preventing damage to the circuit case and the control board therein and facilitating the assembling work and the maintenance inspection work from above.

In order to satisfy the demands relating to the first object, the inventors of the present invention, in the heat pump type dryer in which the auxiliary heat exchanger and the condenser are connected in series in the related art, in accordance with the above circumstances, the amount of heat radiation from the auxiliary heat exchanger. This connection structure was found to be an appropriate amount.

That is, the first invention is a compressor installed in the housing, the accommodating portion for accommodating a drying object, a circulating air passage through the accommodating portion, and a compressor connected to form a flow path through which the refrigerant circulates. And a heat pump apparatus having a condenser, a throttling mechanism and an evaporator.

The dryer is further provided with an auxiliary heat exchanger which is provided outside the ventilation path and connected in series with the flow path in the condenser or in parallel with the condenser, and cooling means capable of cooling the auxiliary heat exchanger. It is to be done.

As used herein, the term "cooling means" includes means for directly cooling by blowing air, water flow, and the like, and means for cooling indirectly by exchanging air in the housing or the like.

In addition, "the flow path in a condenser" means at least one part of the flow path which continues from the upstream end connected to the discharge side of a compressor via a refrigerant pipe to the downstream end connected to the inflow side of a throttling mechanism.

According to the present invention, the auxiliary heat exchanger is connected in series with the flow path in the condenser, connected in parallel with the condenser, or connected, and cooled by cooling means provided outside the ventilation path.

That is, when the configuration in which the auxiliary heat exchanger is connected in series with the flow path in the condenser is applied, the refrigerant introduced into the condenser passes through all the flow paths in the condenser and flows to the throttling mechanism. Via. Therefore, it can radiate heat from the refrigerant | coolant which is heat-exchanging with the air in a ventilation path in a condenser.

That is, by dissipating the air in the ventilation path from the refrigerant heated to the middle, the auxiliary heat exchanger flows as much as the remaining amount of heat used to complete the heating, compared to the configuration in which the auxiliary heat exchanger is connected immediately downstream of the condenser. The amount of heat that can radiate heat from the refrigerant can be large. Therefore, when the cooling means is operated, sufficient heat dissipation amount cannot be ensured, and the situation such as overheating and overpressure of the refrigerant can be prevented.

On the other hand, as compared with the configuration in which the auxiliary heat exchanger is connected directly to the upstream side of the condenser, the amount of heat that can be radiated from the refrigerant can be reduced by the amount of heat used for heating up to the middle. Therefore, when the cooling means is operated, it is possible to prevent the heat from dissipating more than necessary and disturb the heating of the air.

In addition, the "condenser" here includes what consists of a some heat exchanger. For example, you may comprise a condenser with the 1st condenser and the 2nd condenser formed as a heat exchanger separate from the said 1st condenser. In that case, the auxiliary heat exchanger is connected in series between the first condenser and the second condenser. That is, the refrigerant passing through the first condenser flows into the second condenser after passing through the auxiliary heat exchanger provided outside the ventilation path.

In addition, when the structure which connects an auxiliary heat exchanger in parallel with a condenser is applied, the refrigerant which passed through the compressor flows in the upstream side immediately upstream of a condenser, and the branched one passes through a condenser, and the other branched side assists. Pass through the heat exchanger. Therefore, it is possible to radiate heat from the refrigerant of the other branch.

That is, at least a part of the refrigerant discharged from the compressor passes through the auxiliary heat exchanger without flowing through the condenser, so that the amount of the refrigerant passing through the auxiliary heat exchanger as compared with the configuration in which the auxiliary heat exchanger is connected immediately downstream of the condenser. The amount of heat that can be radiated from the refrigerant flowing through the auxiliary heat exchanger can be large. Therefore, when the cooling means is operated, sufficient heat dissipation amount cannot be ensured, and the situation such as overheating and overpressure of the refrigerant can be prevented.

On the other hand, compared with the configuration in which the auxiliary heat exchanger is connected directly upstream of the condenser, the amount of the refrigerant amount not passing through the auxiliary heat exchanger is passed to the other part of the refrigerant flowing out of the compressor, without passing through the auxiliary heat exchanger. As a result, the amount of heat that can be radiated from the refrigerant can be reduced. Therefore, when the cooling means is operated, it is possible to prevent the heat from dissipating more than necessary and disturb the heating of the air.

In this way, both of the above configurations increase the amount of heat dissipation compared to the configuration in which the heat dissipation amount may be insufficient (a configuration in which the subsidiary heat exchanger is provided immediately downstream of the condenser) while the amount of heat dissipation may be excessive (auxiliary). The heat dissipation amount can be reduced rather than the configuration in which the heat exchanger is provided immediately upstream of the condenser. Therefore, the dryers according to the two configurations can prevent a situation in which the amount of heat dissipation from the auxiliary heat exchanger is insufficient or excessive, respectively. As a result, the amount of heat required for heating the air flowing in the ventilation path is reduced. The amount of heat dissipation can be appropriately set so as to prevent overheating and overpressure of the refrigerant.

In addition, the said two structures do not require the member corresponded to a switching valve similarly to the conventional structure of the said patent document 1 in both. For this reason, manufacturing cost can be suppressed only by the quantity of the said member and its control system. Moreover, since it is not necessary to make the cooling performance of a cooling means variable, it is also possible to suppress manufacturing cost further by that much.

In the conventional structure described in the patent document 1, after branching the flow path from the compressor to two to continue to the condenser and the auxiliary heat exchanger, by adjusting the amount of refrigerant flowing to the auxiliary heat exchanger by the switching valve provided in the branch, The amount of heat dissipation by natural heat dissipation from the auxiliary heat exchanger is controlled. However, since the above two configurations both provide such switching valves or do not vary the cooling performance of the cooling means, the amount of heat dissipation when the cooling means is operated to cool the auxiliary heat exchanger is appropriate. Even if the cooling performance of the cooling means is changed or a member similar to the switching valve is provided, it can be configured to be simpler and cheaper than the conventional configuration.

In addition, since both of the above two configurations can take shorter flow path lengths required for the refrigerant to circulate than the conventional configurations in which the auxiliary heat exchanger is connected in series with the condenser, the load applied to the compressor is thereby reduced. In addition, the heat pump apparatus can be configured to be inexpensive.

In addition, the effect exerted by the two configurations is particularly effective in achieving an appropriate amount of heat dissipation when the cooling means is operated to cool the auxiliary heat exchanger, but these two configurations operate the cooling means. It is advantageous to make the amount of heat dissipation suitable even when naturally dissipating heat from the refrigerant flowing in the auxiliary heat exchanger.

According to a second aspect of the present invention, the cooling means includes a cooling fan device that blows air outside the housing toward the auxiliary heat exchanger.

According to the present invention, the cooling fan apparatus directly cools the refrigerant flowing in the auxiliary heat exchanger, and further, the auxiliary heat exchanger, by blowing toward the auxiliary heat exchanger. By configuring in this way, the dryer suitable for exhibiting the above effects is obtained.

According to a third aspect of the present invention, in the first or second aspect of the present invention, the cooling means includes an exhaust fan device configured to exhaust air inside the housing and outside the ventilation path to the outside of the housing. It is characterized by.

According to the present invention, the exhaust fan apparatus promotes heat dissipation from the auxiliary heat exchanger by discharging air near the auxiliary heat exchanger to the outside of the housing. Therefore, the refrigerant | coolant which flows in an auxiliary heat exchanger and also the said auxiliary heat exchanger can be indirectly cooled. By configuring in this way, the dryer suitable for exhibiting the above effects is obtained.

In addition, the said cooling means may contain either one of the said cooling fan apparatus, and the said exhaust fan apparatus, and may include both.

According to a fourth aspect of the present invention, the compressor is configured such that the compression capacity can be changed so that the temperature of the refrigerant discharged from the compressor increases or decreases.

According to the present invention, when operating the dryer, for example, it is possible to distinguish between the operation method for setting the compression capacity relatively low and the operation method for setting the compression capacity relatively higher than that. In that case, when the former driving method is used, since the refrigerant discharged from the compressor becomes lower than when using the latter driving method, the frequency of operating the cooling means is reduced accordingly, and furthermore, the drying step. The amount of power consumption required to complete the process can be reduced. On the other hand, when hastening to dry a drying object, the time required for completing a drying process can be shortened by setting a compression capacity comparatively high.

In the fifth invention, in any one of the first to fourth inventions, a refrigerant temperature sensor capable of detecting a refrigerant temperature discharged from the compressor is provided in a refrigerant pipe connecting the compressor and the condenser. The means is configured to cool the auxiliary heat exchanger based on the detection result by the refrigerant temperature sensor.

In the flow path through which the coolant circulates, the coolant immediately after the temperature is elevated by the compressor flows to the portion that continues from the compressor to the condenser. Therefore, relatively high temperature and high pressure refrigerant | coolant flows rather than the other part.

According to the present invention, the auxiliary heat exchanger is configured to be cooled based on the refrigerant temperature flowing through such a portion, so that the auxiliary heat exchanger can be cooled at a more proper timing in preventing overheating and overpressure of the refrigerant. do.

In addition, by operating the cooling means in accordance with the refrigerant temperature, for example, immediately after the start of the drying process, when it is determined that the refrigerant is relatively low temperature and low pressure and does not need to cool the auxiliary heat exchanger, the cooling means is not operated. It can be stopped. Therefore, the amount of power consumption can also be reduced.

In the sixth invention, in any one of the first to fifth inventions, the auxiliary heat exchanger is connected in series with respect to a flow path in the condenser, and the condenser is connected to an outlet side of the compressor. A first flow path and a downstream end of the second flow path connected to the throttling mechanism, and a downstream end of the first flow path is connected to an upstream end of the heat dissipation flow path in the auxiliary heat exchanger; The upstream end portion is connected to a downstream end portion of the heat dissipation passage.

According to the present invention, the flow path formed in the condenser is divided into two, the first flow path and the second flow path, and the refrigerant flowing into the condenser includes the first flow path, the heat radiation flow path formed in the auxiliary heat exchanger, and the second flow path. Passed in sequence. In this case, the amount of heat dissipation from the auxiliary heat exchanger can be adjusted by changing the flow path length ratio between the first flow path and the second flow path.

For example, if the first flow path is shortened, the second flow path is taken longer. By doing in this way, the amount of heat consumed by the refrigerant | coolant which passes through a 1st flow path becomes small, and the quantity of heat which can be radiated | emitted from the refrigerant | coolant which flows through a heat radiating flow path can be taken large.

Thus, since the amount of heat dissipation from the auxiliary heat exchanger can be increased or decreased without changing the overall constitution of the condenser, it is advantageous in making the amount of heat dissipation appropriate. Moreover, since it becomes advantageous also in achieving common parts, it also becomes advantageous in suppressing manufacturing cost.

According to a sixth invention, in the sixth invention, the condenser has a plurality of straight pipe portions and a pin end having a plurality of connection pipe portions for connecting one end portions of the straight pipe portions to each other so as to communicate with each other in the straight pipe portions. And a tubular heat exchanger.

According to the present invention, the first flow passage and the second flow passage can be formed in the condenser by changing the shape of one connection pipe portion or by replacing two separate pipes without changing the shape of each straight pipe portion. Therefore, it is advantageous in changing the flow path length ratio between the first flow path and the second flow path, and at the same time, it is also advantageous in achieving common parts and suppressing the manufacturing cost.

Eighth invention is the sixth or seventh invention, the bypass flow path for supplying the refrigerant from the downstream end of the first flow path to the upstream end of the second flow path bypassing the heat dissipation flow path; And a flow passage selecting means for switching the refrigerant from the downstream end of the first flow passage to flow the heat dissipation flow passage or the bypass flow passage.

According to the present invention, when the heat dissipation from the auxiliary heat exchanger is unnecessary, by operating the flow path selection means, the heat dissipation passage in the auxiliary heat exchanger is bypassed to the refrigerant introduced into the condenser, thereby preventing unnecessary heat dissipation from the auxiliary heat exchanger. You can block. By doing so, it is advantageous in securing the amount of heat required to heat the air, and the amount of power consumption required for the operation of the heat pump device and the cooling means can be reduced by the amount of unnecessary heat dissipation. .

9th invention is any one of said 1st invention-5th invention WHEREIN: The said auxiliary heat exchanger is connected in parallel with the said condenser, and the quantity of the refrigerant | coolant discharged from the said compressor flows in the said condenser, or A flow path switching means for switching a predetermined amount of the refrigerant discharged from the compressor to flow the heat dissipation flow path and the remaining amount to flow the condenser is provided.

According to the present invention, when the heat dissipation from the auxiliary heat exchanger is not necessary, by operating the flow path switching means, the entire amount of the refrigerant discharged from the compressor is flowed to the condenser, thereby preventing unnecessary heat dissipation from the auxiliary heat exchanger. By doing so, it is advantageous in securing the amount of heat required to heat the air, and the amount of power consumption required for the operation of the heat pump device and the cooling means can be reduced by the amount of unnecessary heat dissipation. .

According to a fifth aspect of the present invention, when the auxiliary heat exchanger is connected in parallel with the condenser, the flow rate of the condenser side flowing through the condenser and the flow rate flowing through the auxiliary heat exchanger are adjusted. On the other hand, when the auxiliary heat exchanger is connected in series with the flow path in the condenser, a flow rate distribution means capable of adjusting a bypass flow rate for bypassing the auxiliary heat exchanger among the refrigerant discharged from the compressor and a flow rate for flowing the auxiliary heat exchanger. And control means for controlling the cooling means and the flow rate distribution means based on the detection result by the refrigerant temperature sensor.

According to the present invention, in adjusting the amount of heat radiation from the auxiliary heat exchanger, cooling of the auxiliary heat exchanger by the cooling means and adjustment of the amount of refrigerant flowing through the auxiliary heat exchanger can be performed in combination. As the amount of refrigerant flowing through the auxiliary heat exchanger increases, heat dissipation from the auxiliary heat exchanger is promoted, while as the amount of refrigerant decreases, heat dissipation from the auxiliary heat exchanger is suppressed. To be advantageous.

According to an eleventh invention, in the tenth invention, the control means is configured such that when the heat pump apparatus starts to operate, the flow rate is such that the total amount of the refrigerant discharged from the compressor becomes the condenser side flow rate or the bypass flow rate. It is characterized by controlling the distribution means.

Usually, when the heat pump apparatus starts to operate, it is required to heat up the air flowing in the ventilation path as quickly as possible.

According to the eleventh invention, the temperature rise of the air flowing in the ventilation path is promoted by the amount which suppresses the heat radiation from the auxiliary heat exchanger, which is advantageous in satisfying the above requirements.

In the twelfth invention or the eleventh invention, the control means determines whether the refrigerant temperature exceeds a first temperature set higher than a predetermined target temperature based on a detection result by the refrigerant temperature sensor. And when it is determined that the first temperature is exceeded, the condenser-side flow rate or the bypass flow rate is decreased by a predetermined amount, and the flow rate flowing through the auxiliary heat exchanger is increased by the amount of the decrease amount. It is characterized by controlling the flow distribution means.

According to the present invention, when the refrigerant temperature exceeds the first temperature, the flow rate of the amount of the refrigerant flowing from the compressor flowing through the auxiliary heat exchanger is increased, thereby facilitating heat dissipation from the auxiliary heat exchanger, and overheating and overpressure of the refrigerant. In preventing, it is advantageous.

In the thirteenth invention or the eleventh invention or the eleventh invention, the control means determines whether the refrigerant temperature exceeds a first temperature set higher than a predetermined target temperature based on a detection result by the refrigerant temperature sensor. And when it is determined that the first temperature is exceeded, the condenser-side flow rate or the bypass flow rate is decreased by a predetermined amount, and the flow rate flowing through the auxiliary heat exchanger is increased by the amount of the decrease amount. It is characterized by cooling the auxiliary heat exchanger to the cooling means while controlling the flow rate distribution means.

According to the present invention, when the refrigerant temperature exceeds the first temperature, the control to promote heat dissipation from the auxiliary heat exchanger and the cooling of the auxiliary heat exchanger are performed simultaneously, thereby more reliably preventing overheating and overpressure of the refrigerant. In that, it is advantageous.

14th invention is the 12th invention or 13th invention, Comprising: The said control means is based on the detection result by the said refrigerant temperature sensor, Whether the said refrigerant temperature exceeded the 2nd temperature set higher than the said 1st temperature. In addition, when it is determined that the second temperature is exceeded, the condenser-side flow rate or the bypass flow rate is decreased by a predetermined amount, and the flow rate through the auxiliary heat exchanger is increased by the amount of the decrease amount. To control the flow rate distribution means.

According to the present invention, since an increase in the amount of refrigerant flowing through the auxiliary heat exchanger is further increased by receiving a further increase in the refrigerant temperature, it is advantageous in more reliably preventing overheating and overpressure of the refrigerant.

15th invention is any one of the 12th-14th invention, The said control means is based on the detection result by the said refrigerant temperature sensor, The coolant temperature set the 3rd temperature set lower than the said target temperature. When it is determined that the temperature is lower than the third temperature, the flow rate flowing through the auxiliary heat exchanger is decreased by a predetermined amount, and the condenser side flow rate or the bypass flow rate is increased by the amount of the decrease amount. And controlling the flow rate distribution means.

According to the present invention, since a decrease in the amount of refrigerant flowing through the auxiliary heat exchanger is received by receiving the detection of a decrease in the refrigerant temperature, it is advantageous in preventing excessive heat radiation.

As described above, the dryer according to any one of the first to fifteenth inventions is an auxiliary heat exchanger cooled by a cooling means provided outside the ventilation path in series with the flow path in the condenser or in parallel with the condenser. By connecting, the amount of heat dissipation from an auxiliary heat exchanger can be made into an appropriate amount, suppressing manufacture cost, and not becoming excessive or insufficient. Therefore, the performance of a dryer can be improved.

Moreover, in order to satisfy the request concerning a 2nd objective, this inventor etc. provide the air guide integrally formed in the shape along the edge of the downstream side of a ventilation opening with respect to the ventilation duct connected to the air inlet of a drum in the airtight state. The air guide is configured to have a guide portion inclined toward the upstream direction toward the direction away from the air vent, so that the drying air introduced from the fan apparatus into the blow duct is guided to the air inlet along the guide portion. .

That is, the sixteenth invention, in the circulation dryer, has an air inlet through which air for drying is introduced, a drum accommodating clothes, and a ventilation port connected to the air inlet of the drum in a hermetic state on the downstream end side. A ventilation duct serving as a ventilation path of the drying air, a fan device connected in an airtight state to an upstream end side of the blowing duct, and sending the drying air into the blowing duct, and directly upstream of the fan device A heat exchanger installed in the heat exchanger to heat and dry the drying air discharged from the drum, wherein the blower duct has an air guide integrally formed in a shape along an edge portion downstream of the vent port. The guide has a guide portion inclined toward the upstream side toward a direction spaced from the vent, to the fan apparatus. Emitter fed along the parts of the drying air to the guide, characterized in that it is adapted to be introduced into the air induction port.

The dryer according to the present invention has an air guide in which a blower duct of the dryer is integrally formed in a shape along the edge of the downstream side of the vent, and the drying air fed into the blower duct from the fan device is led to the air inlet along the air guide guide. It is configured to be. With such a configuration, since the drying air fed from the fan apparatus to the blower duct flows along the air guide guide portion and is guided to the air inlet port, it is possible to suppress the occurrence of swirl flow in the blower duct and efficiently to dry the air in the drum. Can be sent. That is, the pressure loss in the ventilation path between the fan apparatus and the air inlet port of the drum can be reduced. Thereby, compared with the case where no air guide is provided, the rotation speed of the fan apparatus which is necessary in order to ensure the equivalent circulation air volume can be reduced. That is, compared with the case where the air guide is not provided when compared with the same drying performance, the noise reduction and the use energy can be realized. In addition, since the air guide is integrally provided in the blowing duct (for example, integrally formed by resin molding or the like), the cost can be reduced as compared with the conventional dryer having the air guide.

According to a sixteenth invention, in the sixteenth invention, the fan apparatus includes a fan casing having a blowout port connected to an upstream end of the blowing duct in an airtight state, and the air guide includes the fan from the guide portion. It is characterized by including the induction part which extends continuously to the blowing port of a casing, and guides the said drying air introduced into the said blowing duct from the said fan apparatus toward the said air inlet port side.

According to the present invention, the drying air fed into the blowing duct from the fan device is guided to the air inlet side by the guide section of the air guide, and then guided to the air inlet along the air guide guide section. Thereby, the drying air fed into the blowing duct can be guided to the air inlet more effectively.

18th invention is a 17th invention WHEREIN: The edge part of the said fan casing side of the guide part of the said air guide, and the edge part of the ejection outlet side of the said fan casing are comprised so that the height of the surface of each other on the said ventilation path side may be the same. It is characterized by being.

According to the present invention, at the fan casing side end of the guide portion of the air guide and the ejection outlet side end of the fan casing, the heights of the surfaces on the ventilation path side are the same, and the air guide and The fan casing is connected. Thereby, the flow of air in this connection part becomes smooth, and generation | occurrence | production of a noise is suppressed. In addition, leakage of air from this connection portion can also be effectively prevented.

According to a nineteenth aspect of the invention, in the seventeenth or eighteenth aspect, a space is provided between an outer wall of the blower duct and the air guide.

According to the present invention, by providing a space (air layer) between the air duct outer wall (outer circumferential side surface) and the air guide, noise generated in the air duct can be prevented from leaking from the outer wall of the air duct. In addition, since the drying air does not directly contact the outer wall of the blower duct, the heat of the drying air does not contact the atmosphere through the outer wall, so that a heat insulating effect can also be obtained. Therefore, compared with the case where no air guide is provided, the noise reduction and the use energy can be realized.

20th invention is any one of the said 17th invention-19th invention, Comprising: The said air blowing duct has a seal part which makes the inside of the said air blowing duct airtight, The said seal part is outside the said air guide. It is characterized by being installed.

According to the present invention, since the seal portion of the blower duct is provided outside the air guide, the flow of drying air guided from the fan device to the air inlet of the drum through the blower duct is not impeded. Moreover, since it is possible to prevent the pressure of the drying air from being directly applied to the seal portion by using such a configuration, the seal portion can also be improved in practicality.

In a twenty-first invention, in any one of the sixteenth to twentieth inventions, the air guide guide portion is an arc-shaped curved surface concave in a direction away from the ventilation path.

According to this invention, by making an air guide guide part into the arc-shaped curved surface, the drying air sent from the fan apparatus to the blowing duct can be guided more effectively to the air inlet of the drum.

In this way, the dryer according to any one of the sixteenth to twenty-first aspects of the present invention provides an air guide having a guide portion integrally formed in a shape along the edge of the downstream side of the ventilation port, thereby providing an air guide from the fan apparatus to the air inlet port of the drum. Since the pressure loss in the ventilation path between them can be reduced, it becomes possible to suppress the rotation speed of a fan apparatus, and can achieve both reduction of a drying time, reduction of a noise, and energy saving at low cost. Therefore, the performance of a dryer can be improved.

Moreover, in order to satisfy the request concerning 3rd objective, this inventor etc. made it support the circuit case from below by the support member fixed to the housing.

Specifically, the twenty-second invention has a substantially rectangular parallelepiped housing having a front plate, a rear plate, a ceiling plate, a bottom plate and a pair of side plates, and having an opening for opening and receiving a drying object in the front plate, and rotatable in the housing. And a substantially bottomed cylindrical drum housed to be opened on the inlet side, a heating device for heating the air, and an air disposed below the drum to blow the air heated by the heating device via the drum. A blower is provided, and it is related with the dryer provided with the control circuit unit which controls the said blower.

According to a twenty-second aspect of the present invention, the control circuit unit has a substantially plate-shaped inclined surface portion and is located at one side plate side corner portion in the space between the drum and the ceiling plate, and the inclined surface portion is disposed at the one side plate side. And a support member fixed to the housing in a state inclined downwardly toward the housing, a circuit case provided on the surface of the half drum side of the inclined surface portion of the support member, and a control board housed in the circuit case.

As a result, since the circuit case is supported by the support member from below, even if a force is applied from the side of the semi-support member to the circuit case during assembling work such as wiring from above and during maintenance work or transportation, the circuit case and its The control board inside is hard to be damaged. Therefore, the assembling work, maintenance inspection work, and transportation become easy. In addition, since the supporting member is interposed between the circuit case and the drum, damage to the circuit case and the control board therein due to the contact of the rotating drum is prevented.

Moreover, since a support member is arrange | positioned at one side plate side corner part, a support member can be arrange | positioned below compared with the case where it arrange | positions in the center part between both side plates in which the space between a drum and a ceiling plate is narrowed. Therefore, it becomes possible to make the dimension of the control board provided in the half drum side of a slope surface part high, and the dimension of a control board and the freedom degree of a layout become high.

Moreover, since the inclined surface part of a support member is inclined downward toward the said one side plate side, compared with the case where it was horizontal, the inclined surface part can be arrange | positioned downward in the vicinity of the said one side plate. Therefore, especially in the vicinity of the said one side plate of the inclined surface part, it becomes possible to make the dimension of the control board provided in the half drum side of the inclined surface part high, and the freedom of the dimension and layout of a control board becomes high.

Further, in the twenty-second invention, in the twenty-second invention, a reinforcing plate provided in the housing so as to face the plate surface in the front-rear direction from the front of the drum, and in the vicinity of the upper end of the central portion of the reinforcing plate and the rear plate of the housing, It further comprises an interlocking reinforcing member, wherein the supporting member is fixed to the one side plate of the housing and the reinforcing member.

Thereby, since the support member is supported from both sides by the side plate of the housing and the reinforcement member, fall of the support member by vibration etc. is more reliably prevented compared with the case where it supports only on one side. In addition, since the strength of the support member is increased at the fixing position of the side plate and the reinforcing member, the deformation of the support member due to vibration during transportation or operation is more reliably prevented and supported, as compared with the case where the support member is fixed only by the side plate. The weight of the parts that can be installed in the member increases, so that the degree of freedom of the layout of the control parts arranged in the housing is increased.

According to a twenty-fourth invention, in the twenty-third invention, the support member is further fixed to a rear plate of the housing.

Thereby, since the support member is supported from three directions by the side plate, the back plate, and the reinforcement member of a housing, fall of the support member by vibration etc. is prevented more reliably. In addition, since the strength of the support member is increased at the fixing positions of the side plate, the rear plate and the reinforcing member, the deformation of the support member due to vibration during transportation or operation, etc. is more reliably prevented, and the weight of the parts that can be installed on the support member. This increase increases the degree of freedom of the layout of the control components arranged in the housing.

In the twenty-fifth aspect of the present invention, in any one of the twenty-second to twenty-fourth invention, the circuit case is formed in a substantially low plate shape by a plate-shaped bottom wall portion and a circumferential wall portion protruding from the periphery of the bottom wall portion. It has a case main body, is provided in the inclined surface part of the said support member in the state which opened the side of the said case main body toward the half inclined surface part, The said control circuit unit is further provided with the cover member which covers the said control board from the half inclined surface part side. It is characterized by.

As a result, even when water enters the housing from the gap between the side plate and the top plate, the cover member prevents the water from being applied to the control board, thereby preventing corrosion of the control board and short circuit of the circuit. In addition, the cover member also prevents the fluff from the object to be dried, such as clothes or sheets, from adhering to the control substrate, thereby preventing the problem of the control substrate due to the attachment of the fluff.

In a twenty-sixth aspect of the present invention, the cover member is fixed to at least one of the support member and the circuit case.

As a result, since the cover member is fixed to at least one of the support member and the circuit case, separation of the cover member due to vibration or the like is prevented.

In the case where the cover member is fixed only by the support member, it is not necessary to provide the fixing portion with the cover member in the circuit case, so that the storage space of the control board in the circuit case can be increased.

When the cover member is fixed to the circuit case, the installation of the circuit case and the supporting member can be performed in a state where the cover member and the circuit case are fixed to each other, that is, the control board is protected by the cover member. Problems with the control board due to breakage due to contact or collision with a tool or the like or mixing of foreign matter such as screws can be prevented.

In the case where the cover member is fixed to both the circuit case and the support member, the cover member is more reliably prevented from being detached due to vibration or the like, compared with the case where the cover member is fixed to only one side.

In a twenty-seventh invention, in the twenty-fifth or twenty-sixth aspect, an opening is formed in the cover member.

As a result, heat of the control board is released from the opening of the cover member, thereby preventing excessive temperature rise of the control board.

Further, in the twenty-eighth invention, in the twenty-seventh invention, a protrusion is protruded inward in an upper end portion of the side plate, and a concave groove concave in a semi-projection direction of the circumferential wall portion is formed in the circumferential wall portion of the circuit case. Formed to be inclined downward toward the side wall side of the cover member, wherein the cover member includes a front side wall portion and a rear side wall portion that cover the control substrate from the front side and the rear side, and from the lower end portions of the front side wall portion and the rear side wall portion. The side wall side edge part of the said cover member is located in the lower space of the protrusion part of the said side plate, The opening part of the said cover member has a plate-shaped coupling piece part which protrudes below and couples to the recessed groove of the said circuit case. The cover member is slid along the concave groove while the coupling piece is coupled to the concave groove of the circuit case. Wherein the control board in the process of access to parts of the lower space to pass through it, characterized in that the opening in the side wall of the one side.

Thereby, by guiding the cover member in the direction away from the one side wall in a state where the engaging piece of the cover member is engaged with the concave groove of the circuit case, it can be taken out from the lower space of the protruding portion and removed from the circuit case. On the other hand, at the time of arranging the cover member, a circuit case accommodating a control board is provided in the support member, and the cover member is brought closer to the one side wall in a state in which the engaging piece of the cover member is coupled to the concave groove of the circuit case. By sliding in a direction, it can insert and arrange | position in the lower space of the said projection part.

In this way, since the cover member is also disposed in the space below the protruding portion of the side plate, it becomes possible to enlarge the control board covered by the cover member, and as a result, the degree of freedom of the dimensions and layout of the control board is increased.

Further, in the twenty-ninth invention, in the twenty-eighth invention, the one side plate side end edge of the front side wall portion and the rear side wall portion of the cover member is provided with a coupling recess concave to the other side plate side, and the circuit The circumferential wall portion of the case is characterized in that the engaging portion which engages with the engaging recess portion and regulates the movement of the cover member toward the half support member side and the movement toward the one side plate side is protruded before and after.

Thereby, even if the cover member is fastened to the circuit case in the lower space of the protrusion, the engaging portion of the circuit case restricts the movement of the cover member to the half supporting member side and the movement to the one side wall portion side. Fixing to the circuit case becomes easy. Moreover, since fastening parts, such as a screw, are unnecessary, the number of parts can be reduced by that much.

In the thirtieth invention, in any one of the twenty-fifth to twenty-ninth invention, the circuit case further includes a control component connected to the control board via wiring, and the control component includes the cover member. It is characterized by covering from the half inclined surface part side.

Thereby, it is not necessary to draw out the wiring which connects a control component and a control board to the outer side of a circuit case, and wiring operation becomes easy. In addition, even when water enters the housing from the gap between the side plate and the top plate, the cover member prevents the water from being applied to the control component, thereby preventing the problem of the control component due to the intrusion of water or the attachment of fluff.

In this way, the dryer according to any one of the twenty-second to thirtieth inventions installs a circuit case on a support member fixed to a housing, thereby preventing damage to the circuit case and the control board therein and to the support member. Since the circuit case is supported from below, the assembling work such as wiring from above and the maintenance inspection work become easy. Therefore, the reliability of a dryer can be improved. In addition, since it becomes possible to make the dimension of a control board high, the degree of freedom of the dimension and layout of a control board becomes high. Therefore, the productivity of a dryer can be improved.

As described above, the dryer can reduce the amount of heat dissipation from the auxiliary heat exchanger to an appropriate amount, reduce the drying time, reduce noise and save energy, and prevent damage to the circuit case and the control board therein. Since it can be done, the performance can be improved or reliability can be improved.

1A is a perspective view of the heat pump type dryer according to Embodiment A of the first embodiment, seen from the front side and the right side thereof.

FIG. 1B is a perspective view of the heat pump type dryer shown in FIG. 1A, in which the right side surface of the housing is opened from the right side and the rear side.

2 is a perspective view of the heat pump apparatus applied to the heat pump type dryer according to the aspect A, seen from the front side and the right side thereof.

3 is a schematic diagram showing a ventilation path and a heat pump apparatus in the heat pump type dryer according to the aspect A. FIG.

4A is a schematic diagram showing a main part of a modification of the heat pump type dryer according to the aspect A. FIG.

4B is a schematic diagram showing main parts of a modification different from the modification shown in FIG. 4A.

FIG. 5 is a diagram corresponding to FIG. 4A in the heat pump type drier according to Embodiment B of Embodiment 1. FIG.

FIG. 6: is a figure corresponding to FIG. 4B which shows the modification of the heat pump type dryer which concerns on the said form B. FIG.

FIG. 7: is a block diagram which shows the structure of the control apparatus in the heat pump type dryer which concerns on the said form A. FIG.

FIG. 8 is a block diagram showing the configuration of a control device according to a modification shown in FIG. 4B.

9A is a schematic diagram showing the behavior of the refrigerant temperature with respect to the elapsed time after the start of operation in the heat pump type dryer according to Embodiment C of the first embodiment.

FIG. 9B is an enlarged schematic view of the enclosed portion P in FIG. 9A.

10 is a perspective view of the clothes dryer according to the second embodiment as seen from the inclined rear upper side.

11 is a diagram showing a schematic configuration of a clothes dryer according to the second embodiment.

12 is a conceptual view for explaining the flow of air in the air blowing duct according to the second embodiment.

Fig. 13 is a broken perspective view showing a connecting portion of the blowing duct and the circulation intake port.

It is a perspective view which shows the outer cover of a ventilation duct.

FIG. 1: 5A is sectional drawing along the A-A line of FIG.

FIG. 15B is a cross-sectional view taken along the line B-B in FIG. 14.

It is a perspective view which shows the state which attached the fan casing to the outer cover of a ventilation duct.

It is a side view which shows the state which installed the fan casing in the outer cover of a ventilation duct.

18 is a cross-sectional view taken along the line C-C in FIG.

Fig. 19 is a perspective view of the inclined front side in a state where the top plate of the dryer according to Embodiment A of Embodiment 3 of the present invention is removed.

20 is a diagram corresponding to FIG. 19 with the control circuit unit removed.

FIG. 21 is a schematic cross-sectional view taken along a line A-A in FIG. 19.

FIG. 22 is a schematic cross-sectional view taken along line B-B in FIG. 19.

FIG. 23 is an enlarged view of FIG. 19 showing a control circuit unit perimeter. FIG.

24 is a cross-sectional view taken along the line E-E in FIG. 19 showing the upper part of the dryer.

FIG. 25 is an enlarged cross-sectional view corresponding to FIG. 24 showing a circumference of the reinforcing member in a state where the ceiling plate is removed.

26 is a schematic perspective view of the support member and the cover member.

FIG. 27 is an enlarged cross-sectional view corresponding to part F of FIG. 22.

28 is a perspective view of the supporting member.

29 is a perspective view of the circuit case viewed from the right rear side.

Fig. 30 shows a procedure for fixing the cover member to the circuit case. The left figure is a rear view showing a process of fixing the cover member to the circuit case, and the right figure shows a state where the cover member is fixed to the circuit case. It is a rear view which shows.

31A is a perspective view of the control circuit unit viewed from the right rear side.

FIG. 31B is a cross-sectional view taken along the GI-GI line of FIG. 3A.

FIG. 32: is sectional drawing in the GII-GII line of FIG. 31A of the support member 33 and the circuit case 38. FIG.

FIG. 33A is a diagram corresponding to FIG. 31A of Embodiment B of the third embodiment.

33B is a cross-sectional view taken along the line H-H in FIG. 33A.

FIG. 34A is an equivalent to FIG. 31A of the third embodiment C. FIG.

34B is a cross-sectional view taken along the line I-I of FIG. 34A.

35 is a perspective view of the circuit case of Form D of Embodiment 3 as viewed from the front left side.

36 is a view corresponding to FIG. 27 of Embodiment E of the third embodiment.

FIG. 37 is a view corresponding to FIG. 28 of the form F of the third embodiment. FIG.

38 is a block diagram showing the configuration of a control device in the heat pump type drier of the first embodiment.

EMBODIMENT OF THE INVENTION Hereinafter, Embodiment 1 thru | or 3 of this invention are demonstrated in detail based on drawing. The description of the following preferred embodiments is merely exemplary and is not intended to limit the present invention, its scope of application or its use.

For convenience of explanation, the codes are independent for each embodiment. Therefore, the same code | symbol may be attached | subjected also about the same concept as in other embodiment, or the same code | symbol may be attached also to another concept.

Embodiment 1

First, Embodiment 1 will be described based on the drawings. This Embodiment 1 relates to the structure of Claims 1-20, and is shown in FIGS. 1-9B, FIG. 38, and FIG.

(Form A of Embodiment 1)

Hereinafter, the dryer concerning Embodiment A of Embodiment 1 is demonstrated.

The clothes dryer D shown in FIG. 1A constitutes a dryer (heat pump type dryer) according to the present embodiment. The clothes dryer (D) has a housing (1) having a vertically long, substantially rectangular parallelepiped shape extending in the vertical direction, and has a substantially circular shape in a substantially central portion of the front surface of the housing (1) when viewed from the front front. The clothing input opening (not shown) of the shape is opened. The clothes inlet is opened and closed by a lid 11 provided to be swingable. When the cover part 11 is opened, the clothing C as a drying object can be accommodated in the accommodation space 21 provided in the housing 1 via a clothing | feed opening.

First, the whole structure of the clothes dryer D concerning Embodiment A of this Embodiment 1 is demonstrated.

In addition, on the lower side and the right side of the front surface of the housing 1, an inlet 12 for communicating air and the outside air in the housing 1 is opened, while the upper side of the rear side of the housing 1 is also left (housing 1). In the upper side and the left side when viewed from the rear side, an exhaust port 13 through which air in the housing 1 communicates with outside air is opened separately from the inlet 12.

1B shows a state in which the right side surface of the housing 1 is opened. As shown in FIG. 1B, the drum part 2 which forms the said accommodating space 21 is provided in the upper part in the housing 1. As shown in FIG. This drum part 2 has the drum accommodating part 22 and the drum main body (not shown), and comprises the accommodating part which concerns on the form A of 1st Embodiment. Moreover, the cooling fan apparatus 61, the auxiliary heat exchanger 55, and the compressor 52 are arrange | positioned back and forth in order from the front side in the lower part inside the housing | casing 1, and are arranged.

Specifically, the drum accommodating part 22 is formed in the substantially cylindrical shape extended in the front-back direction, and is connected to the clothing inlet. The drum main body is formed in the bottomed cylindrical shape, and is integrally provided with respect to the drum accommodating part 22, with the opening toward the garment inlet. The drum accommodating part 22 and the drum main body form the accommodating space 21 in the drum part 2.

As shown in FIG. 3, the ventilation pipe 4 is disposed in the housing 1. Both ends of the ventilation pipe 4 are connected so that the space in the ventilation pipe 4 and the accommodation space 21 may communicate. Therefore, the ventilation path 3 formed by the ventilation pipe 4 is comprised as the circulation type flow path which passes through the accommodation space 21.

One end portion of the ventilation path 3 is connected to the accommodation space 21 and is separated from the return-side ventilation path 31 that extends the space in the housing 1 up and down, and this return-side ventilation path 31. Connected to the additional accommodating space 21, the other end portions of the air passage-side ventilation path 33 and the return-side ventilation path 31 and the path-side ventilation path 33 which extend the space in the housing 1 up and down are separated from each other. In addition to the connection, the lower space in the housing 1 has a heating and drying ventilation path 32 extending back and forth.

As shown in FIG. 3, a circulation fan device 7 for circulating air in the ventilation path 3 is disposed in the ventilation path 3. The circulation fan device 7 is provided near the connection portion between the channel side ventilation path 33 and the heating and drying ventilation path 32, and sucks air on the side of the heating and drying ventilation path 32, thereby It is comprised so that discharge may be carried out to the side ventilation path 33 side. Therefore, when the circulating fan device 7 is operated, the air discharged from the heat-drying ventilation path 32 sequentially passes through the path-side ventilation path 33, the accommodation space 21, and the return-side ventilation path 31. After passing, a flow of air is returned to the heat drying ventilation path 32 (see the white arrow in the ventilation path 3 in FIG. 3).

As shown in FIG. 3, the heat drying ventilation path 32 includes an evaporator 51 capable of heat exchange with air flowing through the ventilation path 32, and a condenser capable of heat exchange with air passing through the evaporator 51. From the upstream side (upstream side of the air flow direction in the ventilation path 3) to the downstream side (upstream side of the air flow direction in the ventilation path 3) from the upstream side of the ventilation drying path 32 for heating drying. They are arranged at intervals over each other.

2 and 3, the compressor 52, the evaporator 51, the throttling mechanism 54, and the condenser 53 are each configured to form a flow path through which the refrigerant circulates. 56 is sequentially connected, and the heat pump apparatus 5 which concerns on this embodiment is comprised.

In addition, the front and back in FIG. 2 respectively refer to the front and back in the state which installed the heat pump apparatus 5 in the housing 1, and are the same as the front and back with respect to the clothes dryer D and the housing 1, respectively. Do.

Concretely, the compressor 52 is arrange | positioned outside the ventilation path 3, and is arrange | positioned behind the said intake port 12 in the bottom part in the housing 1. This compressor 52 heats up a pressure by thermally compressing the gas refrigerant sucked in from the intake port (not shown) of an upstream, and discharges it from a discharge port (not shown) of a downstream side. The compressor 52 which concerns on this embodiment is comprised including the inverter circuit which can control the drive frequency, and increases and decreases a compression capability based on the input signal from the control apparatus 100 as a control means which concerns on this form ( Can be changed). For example, by reducing the compression capacity of the compressor 52, it is possible to discharge the refrigerant having a relatively low temperature and low pressure than before reducing the compression capacity.

Moreover, the throttle mechanism 54 is arrange | positioned outside the ventilation path 3 similarly to the compressor 52, and is installed in the vicinity of the bottom part in the housing 1. As shown in FIG. The throttling mechanism 54 lowers the temperature of the liquid refrigerant flowing from the upstream inlet port (not shown) by adiabatic expansion, thereby lowering the temperature to lower the temperature, and then flows it out of the downstream outlet port (not shown).

The evaporator 51 is comprised as a fin and tube type heat exchanger. That is, the evaporator 51 has a plurality of fins (straight pipe portions) 51d formed in a straight pipe shape, indicated by a plurality of fins 51c as heat sinks, and a dashed two-dotted line in FIG. ) And a plurality of connecting pipe portions 51f, and have a substantially rectangular box shape. Each tube 51d extends substantially parallel to each other along the left and right directions so as to pass through the fins 51c. Each connection pipe part 51f is formed as a substantially U-shaped curved pipe part, and one end part of each tube 51d is connected to each other. By this connection, the spaces in the respective tubes 51d communicate with each other to form one flow passage extending in the evaporator 51 while reciprocating along the longitudinal direction of the evaporator 51.

As shown in FIG. 3, both ends of the flow path formed in the evaporator 51 are connected to the outlet of the throttle mechanism 54 and the suction port of the compressor 52, respectively, through the flow path formed in the refrigerant pipe 56. It is. As a result, the refrigerant flowing out of the throttling mechanism 54 is sucked into the compressor 52 after passing through the flow path in the evaporator 51.

The condenser 53 is configured as a fin and tube heat exchanger similarly to the evaporator 51, and includes a plurality of fins 53c, a plurality of tubes 53d formed in a straight tube shape, and each of the tubes 53d. In order to make space communicate with each other, it has a some connecting pipe part 53f which connects one end part of each tube 53d with each other, and has a rectangular box shape. However, unlike the evaporator 51, the flow path formed in this condenser 53 is divided into two, the 1st flow path 57 and the 2nd flow path 58 which are independent from each other instead of one flow path.

Specifically, the two-way tube 53d connected to a predetermined one of the plurality of connection pipe portions 53f is formed in a straight tube shape instead of the connection pipe portion 53f, respectively. It can be connected to the return side extension pipe part 92, respectively. By connecting in this way, in the condenser 53, as shown in FIGS. 2 and 3, one end (upstream end) in the tube 53d connected to the discharge port (discharge side) of the compressor via the refrigerant pipe 56. The first flow path 57 which continues from 53a to the one end (first intermediate end) 53g in the tube 53d connected to the path-side extension pipe part 91, and, separately, the return-side extension pipe part 92. One end in the tube 53d connected to the inlet (inlet side) of the throttling mechanism 54 from the one end (second intermediate end) 53h in the tube 53d connected to the The second flow path 58 that continues to the (downstream end) 53b is formed.

As shown in Fig. 2 and Fig. 3, the first intermediate end 53g of the first flow path 57 is an auxiliary heat exchanger installed outside the ventilation path 3 via the outgoing-side extension pipe portion 91 ( While connected to the upstream side of 55, the second intermediate end 53h of the second flow path 58 is the return-side extension pipe portion 92 separately from the first intermediate end 53g of the first flow path 57. ) Is connected to the downstream side of the auxiliary heat exchanger 55.

Specifically, the auxiliary heat exchanger 55 is formed in a thin rectangular box shape extending along the front surface of the housing 1, and at the bottom of the housing 1, the rear of the inlet 12 and the compressor ( 52) to be positioned in front of. Like the evaporator 51 and the condenser 53, this auxiliary heat exchanger 55 is comprised as a fin and tube type heat exchanger. As shown in FIG. A heat radiation passage 59 is formed. As shown in FIG. 2, the upstream end 55a and the downstream end 55b of this heat dissipation flow path 59 are each said path | route through the return side extension pipe part 91 and the return side extension pipe part 92, respectively. It is connected to the first intermediate end 53g and the second intermediate end 53h. Therefore, the auxiliary heat exchanger 55 is connected in series with the flow path in the condenser 53. In other words, the refrigerant discharged from the compressor 52 and introduced into the condenser 53 is dissipated in the first flow path 57 in the condenser 53, the flow path in the outward-side extension pipe portion 91, and the auxiliary heat exchanger 55. After passing through the flow path 59, the flow path in the return-side extension pipe part 92, and the 2nd flow path 58 in the condenser 53, it flows out from the condenser 53 and flows in into the throttle mechanism 54. do.

Therefore, when the heat pump apparatus 5 is operated, as shown in FIG. 3, the gas refrigerant heated up and discharged by the compressor 52 is first condensed through the condenser 53. At this time, the refrigerant flowing into the condenser 53 passes through the first flow path 57 and then flows out of the ventilation path 3 once, and passes through the heat dissipation flow path 59 in the auxiliary heat exchanger 55. do. The refrigerant having passed through the heat dissipation path 59 is returned to the ventilation path 3 again and flows out of the condenser 53 by passing through the second flow path 58 in the condenser 53. Subsequently, the refrigerant which has become a liquid phase through the condenser 53 is forced down by the throttling mechanism 54 to flow out, and then passes through the evaporator 51 to evaporate. And the refrigerant | coolant which passed through the evaporator 51 and became gaseous state returns to the compressor 52 (refer black arrow of FIG. 3).

The refrigerant circulating in this manner is configured to cool and dehumidify the air with the heat of vaporization generated when passing through the evaporator 51 and to heat the air with the heat of condensation generated when passing through the condenser 53. In addition, the refrigerant flowing into the condenser 53 is radiated and cooled by heat exchange with air outside the ventilation path 3 when passing through the auxiliary heat exchanger 55.

In addition, as shown in FIG. 3, in the refrigerant pipe 56 connecting the compressor 52 and the condenser 53, a coolant temperature flowing in the portion immediately downstream of the compressor 52 can be detected. Refrigerant temperature sensor SW1 is provided.

In addition, a drain hole (not shown) penetrates a portion directly below the evaporator 51 and communicates the heat drying ventilation path 32 and the space outside the ventilation pipe 4 with the bottom of the ventilation pipe 4. This perforation is formed, and the drain hole discharges the condensed water generated when the air flowing through the heat drying ventilation path 32 is dehumidified by the evaporator 51 to the outside of the ventilation path 3.

Moreover, below the ventilation pipe 4, the accommodating dish part (not shown) opened toward upper direction is arrange | positioned. This storage pan part accommodates the condensed water discharged | emitted through the drain hole.

The cooling means 6 which concerns on this embodiment is comprised including the said cooling fan apparatus 61 and the exhaust fan apparatus 62, and is comprised so that the auxiliary heat exchanger 55 can be cooled. The cooling means 6 cools the auxiliary heat exchanger 55 to radiate heat from the refrigerant flowing through the heat dissipation flow path 59 in the auxiliary heat exchanger 55.

The cooling fan device 61 is arrange | positioned so that it may be located between the intake port 12 and the auxiliary heat exchanger 55 in the bottom part in the housing 1, as shown in FIG. The cooling fan device 61 is configured to be capable of blowing air outside the housing 1 introduced through the inlet 12 toward the rear, and is turned on based on an input signal from the control device 100. / OFF control (see FIG. 7). As described above, since the cooling fan device 61, the auxiliary heat exchanger 55, and the compressor 52 are arranged and arranged in order from the front side (see FIG. 1B), the cooling fan device 61 from the cooling fan device 61 Blowing cools the auxiliary heat exchanger 55 and the compressor 52 sequentially and directly.

In addition, the exhaust fan device 62 is disposed immediately in front of the exhaust port 13 in the upper portion of the housing 1 as shown in FIG. 3. The exhaust fan device 62 is configured to allow the air outside the ventilation path 3 in the housing 1 to be discharged to the outside of the housing 1, and similarly to the cooling fan device 61, the control is controlled. Based on the input signal from the device 100, it is ON / OFF controlled (see FIG. 7). As described above, the refrigerant flowing through the auxiliary heat exchanger 55 is configured to radiate heat to the air outside the ventilation path 3 in the housing 1, so that the heat pump device 5 operates to assist the refrigerant. The air near the heat exchanger 55 is heated up by the amount of heat dissipated. In addition, with the operation of the compressor 52, the air near the compressor 52 is also heated up. Therefore, while the operation | operation of the heat pump apparatus 5 continues, the air of the auxiliary heat exchanger 55 and the compressor 52 becomes relatively high temperature compared with the other air outside the ventilation path 3. By operating the exhaust fan device 62, relatively high-temperature air in the vicinity of such an auxiliary heat exchanger 55 and the compressor 52 is discharged, and thereby, from the auxiliary heat exchanger 55 and the compressor 52. Heat dissipation is promoted. That is, the exhaust by the exhaust fan device 62 indirectly cools the auxiliary heat exchanger 55 and the compressor 52.

The clothes dryer D configured as described above is controlled by the control device 100. The control apparatus 100 is comprised by the microcomputer, and performs control which performs the process of drying etc. with respect to the clothing C put into the accommodation space 21 through several preset operation processes.

As shown in FIG. 7, various signals are input to the control device 100. Such a signal includes a detection signal from the refrigerant temperature sensor SW1 and an input signal by a user's operation.

The control device 100 detects the coolant temperature immediately after the temperature is elevated by the compressor 52 by performing various calculations based on the detection signal from the coolant temperature sensor SW1. Then, the cooling means 6 is operated based on the detected refrigerant temperature to cool the auxiliary heat exchanger 55.

The control apparatus 100 also sets the control system of the compressor 52 to one of two methods based on the user's operation (see FIG. 7). Specifically, switching between the energy saving operation method which sets the compression capacity of the compressor 52 relatively low based on the input result to the operation panel SW2 by a user, and the speed operation method which sets it relatively higher than that. can do.

When the energy saving operation method is set, the compression capacity of the compressor 52 is set lower than that of the speed driving method. Therefore, the refrigerant discharged from the compressor 52 becomes relatively low temperature and low pressure by the amount which set the compression capacity low, and reduces the power consumption required to complete drying of the clothing C. FIG.

On the other hand, in the case of setting the speed driving method, the compression capacity of the compressor 52 is set higher than that of the energy saving driving method. Therefore, the refrigerant discharged from the compressor 52 becomes relatively high temperature and high pressure by the amount which set the compression capability high, and reduces the time required to complete drying of the clothing C.

Next, the detail of the operation | movement of the heat pump apparatus 5 and the cooling means 6 at the time of operation | movement of the clothes dryer D comprised as mentioned above, and the amount of heat radiation from the refrigerant | coolant which flows in the auxiliary heat exchanger 55 are demonstrated. do.

When the clothes dryer D which concerns on this embodiment starts operation, the circulation fan apparatus 7 and the heat pump apparatus 5 operate | move.

When the circulating fan device 7 is operated, the immediately upstream side of the circulating fan device 7 in the ventilation path 3 becomes a negative pressure, while the immediately downstream side of the circulating fan device 7 becomes a positive pressure. do. According to this differential pressure, the air in the accommodation space 21 circulates in the ventilation path 3.

In addition, by operating the heat pump device 5, a relatively low temperature refrigerant flows in the flow path in the evaporator 51, while a relatively high temperature refrigerant flows in the flow path in the condenser 53 based on the control system set in the compressor 52. Will flow.

Therefore, the air of the accommodation space 21 is cooled and dehumidified by the evaporator 51 when passing through the heat drying ventilation path 32, and then heated by the condenser 53.

In addition, the coolant which flowed into the condenser 53 while the heat pump apparatus 5 is operating as mentioned above first passes through the 1st flow path 57 in the condenser 53, and is ventilation for heat drying The air flowing through the furnace 32 is heated. The refrigerant passing through the first flow path 57 then passes through the auxiliary heat exchanger 55 outside the ventilation path 3, thereby radiating heat to the air outside the ventilation path 3. The refrigerant having passed through the auxiliary heat exchanger 55 returns to the ventilation path 3 again and passes through the second flow path 58 in the condenser 53 to thereby pass the air in the heating drying ventilation path 32. Heat again

By repeating the above steps, the air circulating in the ventilation path 3 and flowing into the accommodation space 21 is maintained in a state of relatively high temperature and low humidity. The clothing C in the storage space 21 is repeatedly contacted with such air, whereby water contained in the clothing C is evaporated and dried. Water evaporated from the clothing C is condensed and dehumidified by the evaporator 51.

The moisture dehumidified by the evaporator 51 adheres to the surface of the evaporator 51 as condensed water. This attached condensed water is discharged to the outside of the ventilation path 3 through the drain hole, and is accommodated on the accommodating dish part.

While continuously operating the heat pump apparatus 5 as described above, the temperature of the compressor 52 and the air temperature in the housing 1 increase. As the temperature rises, the temperature and pressure of the refrigerant flowing through the condenser 53 and the evaporator 51 also increase. As such, the refrigerant is overheated and overpressured, which may cause problems in the operation of the compressor 52.

Therefore, in the control apparatus 100 which concerns on this embodiment, based on the detection result from refrigerant temperature sensor SW1, the refrigerant temperature just after discharge from the compressor 52 exceeds the predetermined temperature (cooling start temperature), If it is determined that the cooling medium 6 is not overheated or overpressured, the auxiliary heat exchanger 55 is operated by operating the cooling means 6 (that is, the cooling fan device 61 and the exhaust fan device 62). Cool. By cooling the auxiliary heat exchanger 55, heat dissipation from the refrigerant flowing through the heat dissipation flow path 59 in the auxiliary heat exchanger 55 is promoted, and overheating and overpressure of the refrigerant can be prevented. The cooling means 6 cools the auxiliary heat exchanger 55 until the refrigerant temperature becomes below a predetermined temperature (cooling stop temperature). In addition, in this embodiment, the said cooling start temperature is set to the temperature below the refrigerant temperature which can compress a refrigerant | coolant, without interrupting the operation | movement of the compressor 52. FIG. In addition, the said cooling stop temperature is set to the temperature below the said cooling start temperature.

Hereinafter, with respect to the amount of heat dissipation from the auxiliary heat exchanger 55 according to Embodiment A of the first embodiment, a conventional configuration in which an auxiliary heat exchanger is connected in series immediately upstream of the condenser (hereinafter, described as a first conventional configuration) ). In the first conventional configuration, since heat is radiated from the coolant before flowing into the condenser, the heat is dissipated more than necessary depending on the configuration or operating state of the cooling means, which causes a problem in heating the air flowing through the ventilation path. I might do it. On the other hand, in the configuration according to Embodiment A of Embodiment 1, since the cooling means 6 radiates heat from the refrigerant after passing through the first flow passage 57 in the condenser 53, the cooling means 6 passes through the first flow passage 57. The amount of heat that can be radiated from the refrigerant passing through the heat dissipation flow passage 59 is smaller than that of the first conventional configuration by the amount of heat consumed in the heat exchange at the time. In other words, the amount of heat consumed from the refrigerant passing through the first flow path 57, that is, the amount of heat used to heat the air flowing through the ventilation path 3, regardless of the configuration or operating state of the cooling means 6. Is kept constant. Therefore, even if the cooling means 6 is operated, since the air flowing through the ventilation path 3 can be heated relatively more sufficiently than the first conventional configuration, it is possible to prevent a situation such as disturbing heating of the air. have.

Next, with respect to the amount of heat dissipation from the auxiliary heat exchanger 55 according to the present embodiment, it is compared with another conventional configuration (hereinafter, described as a second conventional configuration) in which the auxiliary heat exchanger is connected in series immediately downstream of the condenser. do. In this second conventional configuration, since heat is radiated from the refrigerant after passing through the condenser, it is not possible to directly radiate heat from the relatively high temperature and high pressure refrigerant flowing through the section from the discharge side of the compressor to the downstream side of the condenser. Therefore, even if the cooling means is operated, the amount of heat dissipation from the coolant is insufficient, and the coolant is overheated and overpressured, which may cause trouble to the operation of the compressor. On the other hand, in the configuration according to Embodiment A of the first embodiment, since the cooling means 6 dissipates heat from the refrigerant before passing through the second flow path 58 in the condenser 53, the second flow path 58 is prevented. The amount of heat that can be radiated from the refrigerant passing through the heat dissipation passage 59 is larger than that of the second conventional configuration by the amount of heat consumed for heat exchange when passing therethrough. Therefore, when the cooling means 6 is operated, it is possible to dissipate relatively more sufficiently than the second conventional configuration, thereby preventing overheating and overpressure of the refrigerant, thereby preventing a situation such as causing trouble in the operation of the compressor 52. You can do it.

As described above, the clothes dryer D according to Embodiment A of the first embodiment increases the heat dissipation amount compared to the structure (second conventional configuration) in which the heat dissipation amount may be insufficient, while the heat dissipation amount may be excessive ( The amount of heat dissipation can be reduced as compared with the first conventional configuration. Therefore, the clothes dryer D according to Embodiment A of the first embodiment can prevent a situation in which the heat dissipation amount from the auxiliary heat exchanger 55 becomes insufficient and a situation of becoming excessive, respectively, and as a result, heating The amount of heat dissipation can be adjusted to an appropriate amount so that the heating of the air flowing through the drying ventilation path 32 can be prevented and the overheating and overpressure of the refrigerant can be prevented.

Therefore, the clothes dryer D can improve the performance compared with the conventional structure at the point that the amount of heat radiation from the auxiliary heat exchanger 55 can be made into an appropriate amount.

In addition, the clothes dryer D according to Embodiment A of the first embodiment does not require a member corresponding to the switching valve at the connection portion between the condenser 53 and the auxiliary heat exchanger 55. Therefore, manufacturing cost can be suppressed only by the quantity of the said member and its control system.

In addition, since both the cooling fan apparatus 61 and the exhaust fan apparatus 62 are driven by ON / OFF control, manufacturing cost can be held down as the control system becomes simpler.

In addition, by connecting the auxiliary heat exchanger 55 in series with the flow path in the condenser 53, the auxiliary heat exchanger 55 is connected in series immediately upstream or immediately downstream of the condenser 53. The refrigerant circulating in the heat pump device 5 can take a short path length necessary for the compressor 52, the condenser 53, the throttling mechanism 54, and the evaporator 51. Therefore, the load applied to the compressor 52 can be reduced by taking the path length short. By doing so, the power consumption required for the operation of the clothes dryer D can be reduced. In addition, it is advantageous to configure the heat pump apparatus 5 to be inexpensive.

Moreover, the effect exhibited by the structure concerning Embodiment A of Embodiment 1 is especially effective in making the amount of heat dissipation at the time of operating the cooling means 6, and cooling the auxiliary heat exchanger 55 to an appropriate amount, This configuration is advantageous in making the amount of heat dissipation to an appropriate amount even when naturally dissipating heat from the refrigerant flowing through the auxiliary heat exchanger 55 without operating the cooling means 6.

In addition, as the cooling means 6, both the cooling fan apparatus 61 which cools the auxiliary heat exchanger 55 directly, and the exhaust fan apparatus 62 which accelerates heat dissipation from the auxiliary heat exchanger 55 are all. Since it has been operated, it is advantageous in increasing the amount of heat radiation from the auxiliary heat exchanger 55.

In the first conventional configuration, an increase in the amount of heat dissipation from the auxiliary heat exchanger 55 may cause a problem such as disturbing heating of air, but as described above, the clothes dryer D according to the present embodiment. Can prevent such a situation. Therefore, by increasing the amount of heat dissipation from the auxiliary heat exchanger 55 relatively sufficiently, it is possible to more reliably prevent a situation such as overheating and overpressure of the refrigerant.

By applying the cooling fan device 61, the auxiliary heat exchanger 55 and the outside air can be brought into direct contact with each other, which is advantageous in increasing the cooling performance.

Since the exhaust fan device 62 is provided on the rear surface side of the housing 1, unlike the cooling fan device 61, since there is no fear of interference with the clothes container and the lid 11, the exhaust fan device 62 is disposed. The location can be changed relatively easily. Therefore, the cooling performance can be adjusted relatively easily without increasing or decreasing the drive voltage of the exhaust fan apparatus 62. For example, the compressor 52 and the auxiliary heat exchanger 55 can be brought close to each other by changing the location where the exhaust port 13 and the exhaust fan device 62 are installed from the upper side to the lower side of the rear surface of the housing 1. Can be. By doing so, it is advantageous to exhaust the air in the vicinity of the compressor 52 and the auxiliary heat exchanger 55 as it approaches, and furthermore, the cooling performance of the compressor 52 and the auxiliary heat exchanger 55 is improved. You can increase it. In this way, by arranging the exhaust port 13 and the exhaust fan device 62 on the rear surface side of the housing 1, the cooling performance can be adjusted by changing the arrangement position, so that the parts are shared. It is advantageous in reducing the manufacturing cost.

In addition, since the compression capacity of the compressor 52 can be increased or decreased, the energy-saving operation method in which the compression capacity is set relatively low as described above can be distinguished from the speed driving method in which the compression capacity is set relatively high. have. When the energy saving driving method is set, the refrigerant discharged from the compressor 52 becomes relatively low temperature and low pressure than when the speed driving method is set, so that the frequency of operating the cooling means 6 is reduced accordingly. Furthermore, the power consumption required to complete drying of the garment can be reduced. On the other hand, when the drying of the clothing C is rushing, the time required for completing the drying of the clothing C can be shortened by setting the speed driving method.

Further, in the refrigerant pipe 56 connecting the compressor 52 and the condenser 53, a coolant temperature sensor SW1 for detecting a coolant temperature flowing through the portion is provided at a portion immediately downstream of the compressor 52. Since it was installed, the refrigerant temperature immediately after the temperature was elevated by the compressor 52 can be detected. Since the refrigerant having a relatively high temperature and high pressure flows through this portion, the cooling means 6 can be operated at a more appropriate timing in preventing overheating and overpressure of the refrigerant.

In addition, on the basis of the detection result from the refrigerant temperature sensor SW1, when the refrigerant temperature immediately after discharge from the compressor 52 exceeds a predetermined cooling start temperature, the cooling fan device 61 and the exhaust fan device. Since the 62 is operated, when it is judged that the refrigerant is relatively low temperature low pressure and does not need to cool the auxiliary heat exchanger 55, for example, immediately after starting the drying process, the cooling means 6 ) Can be stopped without operating. Therefore, power consumption can be reduced by the amount of electric power required for driving the cooling fan device 61 and the exhaust fan device 62.

In addition, since the flow path formed in the condenser 53 was divided into two parts into the first flow path 57 and the second flow path 58, the flow path length ratio between the first flow path 57 and the second flow path 58 is determined. By changing, the quantity of heat which can be radiated | emitted from the auxiliary heat exchanger 55 can be adjusted.

For example, by making the flow path length of the 1st flow path 57 shorter, the flow path length of the 2nd flow path 58 is made long by that much. By doing so, the amount of heat consumed by the refrigerant passing through the first flow path 57 for heat exchange becomes small, and the amount of heat capable of radiating heat from the refrigerant flowing through the heat dissipation flow path 59 can be taken large.

In addition, the two tubes 53d to be connected to the backward-side extension tube portion 91 and the return-side extension tube portion 92 instead of the connecting tube portion 53f can be changed from those shown in FIG. 2. By doing so, the flow path length ratio between the first flow path 57 and the second flow path 58 can be changed. That is, even if the whole structure of the condenser 53 and further, the shape of each tube 53d is not changed, the predetermined connection pipe part 53f is routed to the backward-side extension pipe part 91 and the return-side extension pipe part 92. By replacing, the 1st flow path 57 and the 2nd flow path 58 can be formed in the condenser 53. FIG. Therefore, the first flow path 57 and the second flow path 58 can be easily formed in the condenser 53. In addition, it is advantageous in changing the flow path length ratio between the first flow path 57 and the second flow path 58, and also in achieving common parts and suppressing manufacturing costs.

(Modified example of Form A of Embodiment 1)

Hereinafter, the modification of the form A of Embodiment 1 is demonstrated.

Although the condenser 53 comprised with the integral heat exchanger was demonstrated in Embodiment A of the said Embodiment 1, you may comprise the two or more heat exchangers which comprised the condenser 53 separately from each other instead. For example, as shown in FIG. 4A, the condenser 53 includes a first condenser 53 ′ and a second condenser 53 ″ disposed immediately downstream of the first condenser 53 ′. You may also

In this case, in the form A of the said Embodiment 1, the 1st flow path 57 and the 2nd flow path 58 formed in the condenser 53 are the 1st condenser 53 'and the 2nd condenser 53, respectively. It corresponds to the flow path formed in ''). In that case, the heat dissipation flow path 59 in the auxiliary heat exchanger 55 is connected in series with the flow path in the condenser 53, that is, as shown in Fig. 4A, the flow path in the first condenser 53 '. It is connected between the 57 and the flow path 58 in the second condenser 53 ''. By so connecting, the refrigerant flowing into the condenser 53 sequentially passes through the flow path 57 in the first condenser 53 ', the heat dissipation flow path 59, and the flow path 58 in the second condenser 53' '. Done.

In addition, as shown in FIG. 4B, the flow path continued from the first intermediate end 53g is branched, and the refrigerant flowing out from the first intermediate end 53g through the first flow path 57 is transferred to the auxiliary heat exchanger ( A bypass flow path 93 for bypassing the heat dissipation flow path 59 in the supply path 55 and supplying it to the second intermediate end 53h of the second flow path 58 is formed. ) May be installed.

Specifically, as shown in FIG. 4B, the bypass flow passage 93 is formed to communicate the inside of the return side extension pipe portion 91 and the inside of the return side extension pipe portion 92. The flow path selecting means 81 is provided in the vicinity of the bypass flow path 93 and the connection portion in the path-side extension pipe portion 91.

As shown in FIG. 8, the flow path selecting means 81 operates on the basis of a control signal from the control device 100, thereby flowing out of the first intermediate end 53g through the first flow path 57. The used refrigerant is switched to flow through the heat dissipation flow path 59 or the bypass flow path 93.

In such a configuration, when the heat dissipation from the auxiliary heat exchanger 55 is unnecessary, the heat dissipation flow path 59 is bypassed by the refrigerant flowing into the condenser 53 through the control of the flow path selecting means 81. The unnecessary heat dissipation from the auxiliary heat exchanger 55 can be blocked. By doing so, the amount of power required for the operation of the compressor 52 and, furthermore, the cooling means 6 is reduced as much as it is advantageous in obtaining the amount of heat required to heat the air and the unnecessary heat is cut off. You may.

In addition, the form of the 1st flow path 57 and the 2nd flow path 58 formed in the condenser 53 is not limited to the above-mentioned structure. For example, the flow path in the condenser may be three minutes, or two or more auxiliary heat exchangers 55 may be disposed.

(Form B of Embodiment 1)

Next, the clothes dryer (heat pump type dryer) D concerning Embodiment B of Embodiment 1 is demonstrated. Below, the difference between the structure which concerns on Embodiment A of Embodiment 1, and its modification, and the effect exhibited by the difference are demonstrated.

As shown in FIG. 5, the auxiliary heat exchanger 55 which concerns on the form B of Embodiment 1 is connected in parallel with the condenser 53. As shown in FIG. Therefore, the flow passage continued from the downstream side of the compressor 52 is connected to the flow passage leading to the upstream end 53a of the condenser 53 and one end (one end of the downstream side) at the connecting portion. It is branched by the flow path which follows. On the other hand, the flow path continued from the downstream side of the condenser 53 and the flow path continued from the downstream side of the auxiliary heat exchanger 55 are provided immediately upstream of the throttle mechanism 54, as shown in FIG. It is aggregated in another connection part, and the one flow path which continues from this other connection part to the upstream side of the throttle mechanism 54 is formed.

Therefore, while the heat pump apparatus 5 according to Embodiment B of Embodiment 1 is operating, a predetermined amount of refrigerant discharged from the compressor 52 continues to flow in the condenser 53, while the auxiliary heat exchanger 55 ), The remaining amount of the refrigerant discharged from the compressor 52 continues to flow.

And the control apparatus 100 which concerns on Embodiment B of Embodiment 1 is based on the detection result from refrigerant temperature sensor SW1, and the refrigerant temperature immediately after passing through the compressor 52 exceeds the said cooling start temperature. When it determines with that, the cooling means 6 (namely, the cooling fan apparatus 61 and the exhaust fan apparatus 62) is operated in order to prevent overheating and overpressure of a refrigerant | coolant. The cooling means 6 cools the auxiliary heat exchanger 55 until the said refrigerant temperature is less than the said cooling stop temperature.

With regard to the amount of heat dissipation from the auxiliary heat exchanger 55 according to Embodiment B of the first embodiment, the same effects as those of the auxiliary heat exchanger 55 according to Embodiment A of the first embodiment can be obtained. Below, the comparison with a 1st conventional structure is concretely performed. In this 1st conventional structure, there exists a possibility that it may radiate heat more than necessary from the refrigerant | coolant before flowing into a condenser by the above-mentioned circumstances. On the other hand, in the configuration according to Embodiment B of the first embodiment, the predetermined amount of the refrigerant flowing out of the compressor is introduced into the condenser 53 without passing through the auxiliary heat exchanger 55, By the amount, the amount of heat used for heating the air can be obtained. Therefore, even if the cooling means 6 is operated, the amount of heat radiation from the refrigerant flowing through the auxiliary heat exchanger 55 can be made smaller than that of the first conventional configuration. As a result, the amount of heat dissipation becomes excessive, and it is possible to prevent a situation such as disturbing the heating of the air.

Next, a comparison with the second conventional configuration is performed. In this second conventional configuration, since the heat is radiated from the refrigerant after passing through the condenser due to the above-described circumstances, the amount of heat radiation may be insufficient. In the configuration according to Embodiment B of the first embodiment, the auxiliary heat exchanger 55 flows without passing through the condenser 53 with respect to a predetermined amount of the refrigerant discharged from the compressor 52. The amount of heat that can be radiated from the refrigerant can be obtained by the amount of quantification. Therefore, when the cooling means 6 operates, the amount of heat radiation from the refrigerant flowing through the auxiliary heat exchanger 55 can be larger than that of the second conventional configuration. As a result, the amount of heat dissipation becomes insufficient, and furthermore, it is possible to prevent a situation such as causing a problem in the operation of the compressor 52.

In this way, the clothes dryer D according to the form B of the first embodiment is the same as the clothes dryer D according to the form A of the first embodiment, rather than the heat dissipation amount (second conventional configuration) in which the heat dissipation amount may be insufficient. In addition, the heat dissipation amount can be reduced more than the configuration (first conventional configuration) in which the heat dissipation amount may be excessive. Therefore, the clothes dryer D according to Embodiment B of the first embodiment, like the clothes dryer D according to Embodiment A of the first embodiment, interferes with the heating of the air flowing through the heat drying ventilation path 32. The amount of heat dissipation can be set appropriately so that overheating and overpressure of the refrigerant can be prevented.

In addition, the structure which concerns on the form B of Embodiment 1 does not require the member corresponded to a switching valve in the connection part between the condenser 53 and the auxiliary heat exchanger 55. As shown in FIG. Therefore, manufacturing cost can be suppressed only by the quantity of the said member and its control system.

In addition, since the airflow amount from the cooling fan apparatus 61 and the exhaust fan apparatus 62 does not need to be made variable, manufacturing cost can be suppressed by that much.

In addition, since both the cooling fan apparatus 61 and the exhaust fan apparatus 62 are driven by comparatively simple ON / OFF control, it manufactures so that a control system can be simplified rather than the structure which made the air volume variable. The cost can be kept down.

In addition, by connecting the auxiliary heat exchanger 55 in parallel with the condenser 53, the refrigerant circulating in the heat pump device 5 is the compressor 52 and the condenser similarly to the configuration according to Embodiment A of the first embodiment. The length of the flow path required for sequencing 53, the throttling mechanism 54, and the evaporator 51 can be shortened. Therefore, the load to the compressor 52 can also be reduced by taking the flow path length short. By doing so, the power consumption required for the operation of the clothes dryer D can be reduced. In addition, it is advantageous to configure the heat pump apparatus 5 to be inexpensive.

Moreover, the effect exhibited by the structure concerning Embodiment B of Embodiment 1 is especially effective in making the amount of heat radiation at the time of operating the cooling means 6 and cooling the auxiliary heat exchanger 55 suitable amount. In the same manner as in Embodiment A of Embodiment 1, the configuration is such that the amount of heat dissipation is set to an appropriate amount even when the heat dissipation is naturally performed from the refrigerant flowing in the auxiliary heat exchanger 55 without operating the cooling means 6. It is advantageous.

(Modification of Form B of Embodiment 1)

Hereinafter, the modification of the form B of Embodiment 1 is demonstrated.

As a modified example of Embodiment B of Embodiment 1, as shown in FIG. 6, you may provide the flow path switching means 82 in the upstream branch part (connection part).

The flow path switching means 82 flows the entire amount of the refrigerant discharged from the compressor 52 into the condenser 53 based on the control signal from the control device 100 or a predetermined amount of the discharged refrigerant. Is switched to the auxiliary heat exchanger (55) and the remaining amount to the condenser (53).

According to this structure, when the heat dissipation from the auxiliary heat exchanger 55 is unnecessary, the heat dissipation from the auxiliary heat exchanger 55 can be interrupted by flowing the entire amount of the refrigerant discharged from the compressor 52 to the condenser 53. have. By doing so, the amount of power consumption required for the operation of the compressor 52 and, furthermore, the cooling means 6 can be reduced by the amount which is advantageous in heating the air and suppresses unnecessary heat radiation.

(Form C of Embodiment 1)

The following describes the form C of the first embodiment.

In the modification of the form A of Embodiment 1 shown in FIG. 4B, when the auxiliary heat exchanger 55 is connected in series with the flow path in the condenser 53, the bypass flow path 93 and the flow path selecting means are shown. A configuration in which the 81 is provided is disclosed, and the flow path selecting means 81 flows the bypass passage 59 for the heat dissipation in the auxiliary heat exchanger 55 to the refrigerant passing through the first flow path 57. And the flow path through which the heat dissipation flow path 59 passes.

Embodiment C of the first embodiment includes a bypass flow rate Qb that bypasses the auxiliary heat exchanger 55 of the refrigerant discharged from the compressor 52 and passed through the first flow path 57 by the flow path selecting means 81. It is obtained by replacing the heat radiation flow rate Qc flowing through the auxiliary heat exchanger 55 with an adjustable flow rate distribution means.

In this aspect C, the flow rate distribution means is configured as a solenoid valve, and based on the control signal from the control device 100, the ratio Qr (= Qc / Qb) of the heat radiation flow rate Qc to the bypass flow rate Qb, It can be changed in the range of 0 to 100%. For example, when the ratio Qr = 0%, the auxiliary heat exchanger 55 is bypassed to the total amount Qt of the refrigerant passing through the first flow path 57, while when the ratio Qr = 100%, the first flow path ( The heat dissipation flow path 59 in the auxiliary heat exchanger 55 flows to the total amount Qt of the refrigerant passing through 57. In addition, the heat radiation flow rate Qc increases monotonously as the ratio Qr increases from 0% to 100%.

In addition, as the heat dissipation flow rate Qc increases, heat dissipation from the auxiliary heat exchanger 55 is promoted, while as the heat dissipation flow rate Qc decreases, the heat dissipation from the auxiliary heat exchanger 55 is suppressed.

In this embodiment C, the amount of refrigerant flowing through the

flow paths

57 and 58 in the condenser 53 is kept constant regardless of the magnitude of the ratio Qr.

The control apparatus 100 which concerns on this form C is comprised so that the cooling means 6 and the flow volume distribution means may be controlled based on the detection result by the refrigerant temperature sensor SW1.

Such a configuration is obtained by replacing the flow path selecting means 81 with the flow rate distribution means in FIGS. 4B and 8.

The control device 100 according to this embodiment C controls the flow rate distribution means so that when the heat pump device 5 starts to operate, the total amount Qt of the refrigerant discharged from the compressor 52 becomes the bypass flow rate Qb. .

And the control apparatus 100 determines whether a refrigerant | coolant temperature exceeded the 1st temperature T1 set higher than predetermined target temperature T0 based on the detection result by refrigerant temperature sensor SW1, When it is determined that one temperature T1 has been exceeded, the flow rate distribution means is controlled to reduce the bypass flow rate Qb by a predetermined amount ΔQ and increase the heat radiation flow rate Qc flowing through the auxiliary heat exchanger 55 by the amount of the decrease amount ΔQ. . The first temperature T1 in this embodiment C corresponds to the cooling start temperature in the above embodiments A to B. FIG.

The control device 100 also operates the cooling means 6 when performing such control. The control device 100 cools the auxiliary heat exchanger 55 with the cooling means 6 until the coolant temperature is lower than the target temperature T0. The target temperature T0 in this form C is equivalent to the cooling stop temperature in the said forms A-B.

Further, the control device 100 determines whether or not the coolant temperature exceeds the second temperature T2 set higher than the first temperature T1 based on the detection result by the coolant temperature sensor SW1, and the second When it determines with exceeding temperature T2, a flow volume distribution means is controlled so that bypass flow volume Qb is further reduced by predetermined amount (DELTA) Q, and the heat radiation flow volume Qc is further increased by the quantity of the decrease amount (DELTA) Q.

On the other hand, the control apparatus 100 determines whether or not the refrigerant temperature is lower than the third temperature T3 set lower than the target temperature T0 based on the detection result by the refrigerant temperature sensor SW1, and the third temperature T3. When it is determined that the ratio is less than, the flow rate distribution means is controlled to reduce the heat radiation flow rate Qc by the predetermined amount ΔQ and increase the bypass flow rate Qb by the amount of the decrease amount.

Moreover, the control apparatus 100 which concerns on this form C is comprised so that the compression capacity of the compressor 52 can be increased or decreased based on the detection result by refrigerant temperature sensor SW1, and the cooling means 6 By combining control, control of the flow rate distribution means, and control of the compressor 52, the refrigerant temperature, and further, the temperature of the air flowing in the ventilation path 3 are configured to be kept constant.

Hereinafter, an example of control using the control apparatus 100 comprised as mentioned above is demonstrated.

9A schematically shows the behavior of the refrigerant temperature with respect to the elapsed time t after the start of operation in the clothes dryer D. FIG.

When the clothes dryer D starts operation, the control apparatus 100 is a drying process, as shown in FIG. 9A, the heating process for raising a refrigerant temperature as soon as possible, and the refrigerant | coolant temperature as predetermined predetermined temperature T0. It is comprised so that a constant temperature process for maintaining in the vicinity may be performed one by one.

First, the control apparatus 100 performs a heating process over predetermined time t0 (0 <= t <t0).

In the warming step, the total amount Qt of the refrigerant discharged from the compressor 52 is the bypass flow rate Qb (Qr = 0%), whereby the heat radiation flow rate Qc is reduced to the maximum. Therefore, in this overtemperature process, the temperature of a refrigerant | coolant and further heating of the air which flows through the ventilation path 3 can be performed as soon as possible.

In addition, in this heating process, the compression capacity of the compressor 52 is set relatively high in order to perform heating of air as quickly as possible.

And the control apparatus 100 transfers from a heating process to a constant temperature process when predetermined time t0 passes (t≥≥t0) after starting a drying process.

In the constant temperature step, the control device 100 determines that the coolant temperature exceeds the first temperature T1 (t = t1) as shown in FIG. 9B in which the enclosed portion P of FIG. 9A is enlarged. The bypass flow rate Qb is decreased by ΔQ (Qb = Qt−ΔQ), and the heat radiation flow rate Qc is increased from zero by ΔQ (Qc = ΔQ). By doing so, heat dissipation from the auxiliary heat exchanger 55 is promoted, and an increase in the refrigerant temperature is suppressed. In addition, the control apparatus 100 performs control to increase the heat radiation flow rate Qc and cools the auxiliary heat exchanger 55 to the cooling means 6 until the refrigerant temperature is lower than the target temperature T0.

As shown in FIG. 9B, the control device 100 increases the heat radiation flow rate Qc by ΔQ every time the coolant temperature exceeds the first temperature T1 (t = t2, t3), and cools. It is adapted to operate the means 6.

By the way, generally, as a drying process advances, a refrigerant temperature becomes easy to rise gradually. Therefore, even if the heat radiation flow rate is increased by ΔQ and the cooling means 6 is operated, the coolant temperature may not decrease until the coolant temperature is lower than the first temperature T1.

In order to cope with such a case, when the control apparatus 100 determines that the refrigerant temperature exceeds the second temperature T2 set higher than the first temperature T1 (t = t4), the bypass flow rate Qb is again ΔQ. Decrease, and increase the heat radiation flow rate Qc again by ΔQ.

On the other hand, when the control apparatus 100 determines that the amount of heat dissipation from the auxiliary heat exchanger 55 becomes excessive and the refrigerant temperature is lower than the third temperature T3 set lower than the target temperature T0 (t = t5), In order to suppress heat radiation, the heat radiation flow rate Qc is decreased by ΔQ and the bypass flow rate Qb is increased by ΔQ.

As shown in FIG. 9B, the control device 100 reduces the heat radiation flow rate Qc by ΔQ each time the coolant temperature is lower than the third temperature (t = t6).

In addition, the control apparatus 100 is comprised so that the compression capability of the compressor 52 may gradually decrease as a drying process advances. By doing in this way, the rise of the refrigerant temperature accompanying advancing of a drying process is suppressed as much as possible. In this example, when the constant temperature step is divided into two parts of the first half and the second half, the compression capacity is set relatively high in the heating step and the first half of the constant temperature step, while the compression capacity is set lower in the latter part of the constant temperature step. have.

In addition, the control device 100 increases the heat radiation flow rate Qc to the maximum (Qr = 100%) and, even when the cooling means 6 is operated, when the refrigerant temperature does not fall below the target temperature T0, the compressor 52 By lowering the compression capacity of), the refrigerant temperature is lowered.

In addition, the control device 100 reduces the heat radiation flow rate Qc to a minimum (Qr = 0%), and when the coolant temperature still does not exceed the target temperature T0 even when the operation of the cooling means 6 is stopped. By raising the compression capacity of 52, the refrigerant temperature is raised.

Thus, the control apparatus 100 which concerns on this form C combines the operation | movement of the cooling means 6, the control of a flow distribution means, and the control of the compressor 52, and it makes a refrigerant temperature near target temperature T0. It is configured to keep on.

As described above, since the clothes dryer D according to the form C is configured to increase or decrease the heat radiation flow rate Qc through the control of the refrigerant distribution means, the amount of heat radiation from the auxiliary heat exchanger 55 is adjusted to an appropriate amount. In that, it is advantageous.

Moreover, since the clothes dryer D which concerns on the form C is comprised so that the whole quantity Qt of the refrigerant discharged | emitted from the compressor 52 may become bypass flow volume Qb, when the heat pump apparatus 5 starts operation | movement, It is advantageous to suppress heat radiation from the heat exchanger 55 and to raise the temperature of the air flowing in the ventilation path 3 as quickly as possible.

In addition, since the clothes dryer D according to Form C is configured to simultaneously increase the heat radiation flow rate Qc and operate the cooling means 6 when the refrigerant temperature exceeds the first temperature T1, the refrigerant temperature. The rise can be suppressed while lowering. Therefore, it is advantageous to more reliably prevent overheating and overpressure of the refrigerant.

In addition, since the clothes dryer D according to the form C is configured to further increase the heat radiation flow rate Qc when the refrigerant temperature exceeds the second temperature T2, the amount of heat radiation from the auxiliary heat exchanger 55 is increased to an appropriate amount. Thus, it is advantageous to more reliably prevent overheating and overpressure of the refrigerant.

In addition, since the clothes dryer D according to the form C is configured to reduce the heat radiation flow rate Qc when the refrigerant temperature is lower than the third temperature T3, it is advantageous in preventing excessive heat radiation.

In addition, since the clothes dryer D according to the form C is configured to decrease the compression capacity of the compressor 52 as the drying process proceeds, the clothes dryer D is combined with the control of the flow distribution means and the operation of the cooling means. By using it, it becomes advantageous in controlling the amount of heat dissipation from an auxiliary heat exchanger finely and precisely, and making it an appropriate amount.

(Form D of Embodiment 1)

The following describes the form D of the first embodiment.

In the modification of the form B of Embodiment 1 shown in FIG. 6, when the auxiliary heat exchanger 55 is connected in parallel with the condenser 53, the structure which provided the flow path switching means 82 is started, The flow path switching means 82 flows the entire amount of the refrigerant discharged from the compressor 52 into the condenser 53, or flows a predetermined amount of the discharged refrigerant into the auxiliary heat exchanger 55, and also the remaining amount. It is comprised so that switching to the condenser 53 can be carried out alternatively.

The form D of Embodiment 1 has the flow path switching means 82 passing through the condenser side flow volume Qv which flows through the condenser 53 among the refrigerant | coolants discharged from the compressor 52, and the heat radiation flow volume Qc which makes the auxiliary heat exchanger 55 pass. It is obtained by replacing with an adjustable flow rate distribution means.

In this aspect C, the flow rate distribution means is configured as a solenoid valve similarly to the aspect D, and based on a control signal from the control device 100, the ratio Qr (= Qc) of the heat radiation flow rate Qc to the condenser side flow rate Qv. / Qv) can be changed in the range of 0 to 100%.

The control apparatus 100 which concerns on this modification is comprised so that the cooling means 6 and the flow volume distribution means may be controlled based on the detection result by refrigerant temperature sensor SW1.

Such a configuration is obtained by replacing the flow path selecting means 81 with the flow rate distribution means in FIGS. 6 and 8.

In this case, the flow rate of the refrigerant flowing through the condenser 53 is increased or decreased in accordance with the change of the ratio Qr. For example, as the ratio Qr increases, the flow rate flowing through the condenser side flow rate Qv and further condenser 53 decreases monotonously.

The control apparatus 100 according to the form D of the first embodiment is configured to be able to execute the same control as the control apparatus 100 according to the form C of the first embodiment.

Therefore, the clothes dryer D according to the form D of Embodiment 1 exhibits the same effects as those described for the clothes dryer D according to the embodiment C of the embodiment.

Here, the following effects are mentioned, for example as another effect with the clothes dryer D which concerns on form C of Embodiment 1, and the clothes dryer which concerns on form D.

That is, in the form C, the amount of refrigerant flowing through the heat dissipation passage 59 in the auxiliary heat exchanger 55 can be adjusted through the ratio Qr, while the amount of refrigerant flowing through the

passages

57 and 58 in the condenser 53 is ratio. Irrespective of the magnitude of Qr, it is comprised so that it may remain constant. By this structure, when adjusting ratio Qr, the influence on the heating of the air by the condenser 53 can be suppressed. Therefore, it is advantageous in adjusting the amount of heat dissipation and heating of air at the same time.

Therefore, the clothes dryer D which concerns on the form C has the compression performance of the compressor 52, the cooling performance of the cooling means 6, and the target performance (energy saving property of the clothes dryer D), or drying time. Or the like, etc.), the heat dissipation amount can be easily adjusted without disturbing the drying of the clothing C.

On the other hand, in the form D, the auxiliary heat exchanger 55 can be connected relatively easily regardless of the structure of the

flow paths

57 and 58 in the condenser 53. Therefore, in using heat exchangers other than a fin and tube type as a condenser, it becomes advantageous.

As such a heat exchanger, the microchannel type heat exchanger provided with the micro scale flow path, the S fin type heat exchanger etc. which meandered and bent the piping after expanding the refrigerant piping and contacting it with the fin are mentioned, for example. have. The configuration relating to the form D can be easily applied to a heat exchanger having such a relatively complicated flow path, so that the productivity of the clothes dryer D can be improved.

This effect is similarly exhibited in the form B of the first embodiment.

(Modifications of Forms C and D of Embodiment 1)

Hereinafter, modifications of the form C of the first embodiment and the form D of the first embodiment will be described.

In Embodiment C of Embodiment 1, similarly to the modification of Embodiment A of Embodiment 1, the condenser 53 may be constituted by two or more heat exchangers configured as separate bodies.

In addition, in the said mode C and D, when it determines with refrigerant | coolant temperature exceeding 1st temperature T1, the control apparatus 100 increases the heat radiation flow volume Qc which flows through the auxiliary heat exchanger 55, and also cools 6 ) Is configured to cool the auxiliary heat exchanger 55, but instead of this configuration, only the control for increasing the heat radiation flow rate Qc may be executed without operating the cooling means 6.

By configuring in this way, the amount of heat dissipation from the auxiliary heat exchanger 55 can be adjusted more delicately. Therefore, in making the appropriate amount of heat dissipation from the auxiliary heat exchanger 55, it becomes further advantageous.

In that case, when it determines with the coolant temperature exceeding predetermined 4th temperature (> T0) different from 1st temperature T1, you may make the cooling means 6 operate.

Further, the cooling means 6 may be operated based on a combination of the detection result of the refrigerant temperature sensor SW1, the value of the ratio Qr, the progress of the drying process, and the like.

The predetermined amount ΔQ for increasing or decreasing the bypass flow rate Qb, the heat radiation flow rate Qc, or the condenser side flow rate Qv is also appropriately based on the detection result of the refrigerant temperature sensor SW1, the value of the ratio Qr, the progress of the drying process, and the like. You can change it.

In addition, when it determines with refrigerant | coolant temperature exceeding 1st temperature T1, when ratio Qr is less than predetermined value (for example, 100%), it is assumed that there exists a possibility of increasing bypass flow volume Qb, While only the control is executed, when the ratio Qr is equal to or larger than this predetermined value, it may be assumed that there is no room for increasing the bypass flow rate Qb, and only the operation of the cooling means 6 may be executed.

By configuring in this way, since the operation | movement of the cooling means 6 can be suppressed as much as possible, the drive sound produced by the drive of the cooling fan apparatus 61 and the exhaust fan apparatus 62 is suppressed, or this fan The amount of power consumption required for the operation of the

devices

61 and 62 can be reduced.

These modifications can also be used in combination with each other to the extent possible.

In addition, the control regarding the compressor 52 can also be changed as much as possible.

(Another modification)

Below, the other modified example regarding Embodiments A-D of Embodiment 1 is demonstrated.

The control method by the control apparatus 100 is not limited to the above-mentioned control method, but can be changed as much as possible.

In the above-described embodiment, the cooling means 6 is operated based on the detection signal from the refrigerant temperature sensor SW1 provided in the refrigerant pipe 56 of the heat pump device 5. Instead of the coolant temperature sensor SW1, an air temperature sensor may be provided in the ventilation pipe 4 for detecting the air temperature just before flowing into the accommodation space 21. By doing so, the cooling means 6 can be operated based on the air temperature flowing through the ventilation path 3. Further, by using the refrigerant temperature sensor SW1 and the air temperature sensor in combination, more precise and precise control can be performed when the refrigerant temperature rises. In that case, for example, the control for changing the compression capacity of the compressor 52 and the control for operating the cooling means 6 may be performed in combination. In Embodiments A to B of Embodiment 1, the cooling start temperature and the cooling stop temperature can be appropriately changed depending on the configuration of the clothes dryer D and the like.

In the above embodiment, the cooling fan device 61 and the exhaust fan device 62 are operated at the same time when the cooling means 6 operates, but the present invention is not limited to this configuration. For example, either the cooling fan device 61 or the exhaust fan device 62 may be operated.

In addition, the cooling means 6 is not limited to what includes the cooling fan apparatus 61 and the exhaust fan apparatus 62. For example, as the cooling means 6, only the exhaust fan apparatus 62 may be arrange | positioned. As described above, by installing the exhaust fan device 62 on the rear surface side of the housing 1, since the exhaust port 13 is not visible from the front side of the housing 1, designability can be improved. have. In addition, compared with the case where it is installed in the front surface side of the housing | casing 1, the drive sound of the exhaust fan apparatus 62 and the aerodynamic noise which generate | occur | produces by inhaling outside air can be reduced.

In addition, as the cooling means 6, you may comprise the water cooling type cooling apparatus instead of the said structure, or in addition to the said structure.

The object to be dried is not limited to the clothing (C). Specifically, you may apply the structure which concerns on embodiment mentioned above to the dish dryer other than the clothing dryer D, for example. In that case, the object to be dried becomes tableware, not clothing (C). It can also be applied to a bathroom dryer.

Moreover, the washing | cleaning process of the clothing C can also be applied to the dry washing machine which can implement.

(Control Method of Embodiment 1)

Hereinafter, the control method of the dryer which concerns on Embodiment 1 is demonstrated.

As shown in FIG. 38, various signals are input to the control apparatus 100. Such a signal includes a detection signal from the refrigerant temperature sensor SW1 and an input signal by the user's operation of the operation panel SW2.

The control device 100 detects the coolant temperature immediately after the temperature is elevated by the compressor 52 by performing various calculations based on the detection signal from the coolant temperature sensor SW1. Then, the cooling means 6 is operated based on the detected refrigerant temperature to cool the auxiliary heat exchanger 55 and to control the flow rate distribution means 83.

The flow rate distribution means 83 is configured to adjust the flow rate for flowing the auxiliary heat exchanger 55 in the refrigerant discharged from the compressor 52.

Specifically, as shown in Fig. 4B, when the auxiliary heat exchanger 55 is connected in series with the flow path in the condenser 53, the flow path selecting means 81 is a flow distribution means 83 of the present control method. Can be. The flow rate distribution means 83 discharges heat from flowing through the bypass flow rate Qb for bypassing the auxiliary heat exchanger 55 of the refrigerant discharged from the compressor 52 and passing through the first flow path 57 and the auxiliary heat exchanger 55. The flow rate Qc is configured to be adjustable.

In addition, as shown in FIG. 6, when the auxiliary heat exchanger 55 is connected in parallel with the condenser 53, the flow path switching means 82 may be the flow distribution means 83 of the present control method. . The flow rate distribution means 83 is configured to adjust the heat dissipation flow rate Qc through which the condenser side flow rate Qv flowing through the condenser 53 and the auxiliary heat exchanger 55 of the refrigerant discharged from the compressor 52 pass.

Next, the control procedure of the clothes dryer D of this embodiment is demonstrated with reference to FIG.

When the user inputs the operation of the clothes dryer D to the operation panel SW2, the control device 100 operates the heat pump device 5 (110).

When the operation of the heat pump apparatus 5 is started, the flow rate distribution means is controlled 120 so that the total amount Qt of the refrigerant discharged from the compressor 52 becomes the bypass flow rate Qb or the condenser side flow rate Qv.

Then, the first detection temperature Ts1 is detected by the refrigerant temperature sensor SW1 (130).

The control apparatus 100 determines whether the 1st detection temperature Ts1 exceeded the 1st temperature T1 set higher than predetermined target temperature T0 based on the detection result by the refrigerant temperature sensor SW1 (140). .

When it is determined that the first detection temperature Ts1 exceeds the first temperature T1, the bypass flow rate Qb or the condenser side flow rate Qv is decreased by a predetermined amount ΔQ, and the heat radiation flowing through the auxiliary heat exchanger 55 by the amount of the decrease amount ΔQ. The flow distribution means is controlled 150 to increase the flow rate Qc. The first temperature T1 corresponds to the cooling start temperature in the forms A to B of the first embodiment.

The control device 100 also operates the cooling means 6 when performing such control (160). The control device 100 cools the auxiliary heat exchanger 55 with the cooling means 6 until the refrigerant temperature is lower than the target temperature T0. The target temperature T0 corresponds to the cooling stop temperature in the forms A to B of the first embodiment.

In addition, the control device 100 detects the second detection temperature Ts2 by the refrigerant temperature sensor SW1 (170).

The control device 100 determines whether or not the second detection temperature Ts2 exceeds the second temperature T2 set higher than the first temperature T1 based on the detection result by the refrigerant temperature sensor SW1 (180), When it determines with exceeding 2nd temperature T2, a flow volume distribution means is made to reduce bypass flow volume Qb or condenser side flow volume Qv again by predetermined amount (DELTA) Q, and to further increase heat radiation flow volume Qc by the quantity of the decrease amount (DELTA) Q. Control (190).

On the other hand, the control apparatus 100 determines whether the 2nd detection temperature Ts2 was lower than the 3rd temperature T3 set lower than the target temperature T0 based on the detection result by the refrigerant temperature sensor SW1 (200), When determining that it is less than the third temperature T3, the heat dissipation flow rate Qc is reduced by a predetermined amount ΔQ, and the flow rate distribution means is controlled to increase the bypass flow rate Qb or the condenser side flow rate Qv by the amount of the decrease amount.

Although not shown in the drawing, the control device 100 may be configured to increase or decrease the compression capacity of the compressor 52 based on the detection result by the refrigerant temperature sensor SW1, By combining the control with the control of the flow rate distribution means and the control of the compressor 52, it can be configured to keep the refrigerant temperature, and further, the temperature of the air flowing in the ventilation path 3 constant.

Embodiment 2

Next, Embodiment 2 will be described based on the drawings.

Embodiment 2 is shown in FIGS. 10 to 18.

Composition of the clothes dryer

The clothes dryer D as the dryer which concerns on Embodiment 2 is provided with the housing 1 which has the shape of the vertically long substantially rectangular parallelepiped extended along an up-down direction. As shown in FIG. 10, the housing 1 includes

side panels

1b and 1b extending in the vertical direction disposed to face each other, and an upper panel that connects between upper ends of both

side panels

1b and 1b. 1a, the base part 1d, and the back panel 1c are provided. The base part 1d connects the lower end parts of both

side panels

1b and 1b and integrally extends upwardly from the rear lower end parts of both

side panels

1b and 1b to both sides. It is comprised so that rear lower sides of) may be connected. The rear panel 1c connects the rear side of both

side panels

1b and 1b, the rear side of the upper panel 1a, and the upper side of the base portion 1d above the rear portion of the housing 1. have. In addition, as shown in FIG. 11, the upper part of the front surface of the housing | casing 1 has a substantially circular clothes input opening 2 open | released from the front front, and this clothing inlet 2 is a cover which can rock | swivel. The opening and closing is performed by the section 3. Moreover, the blowing duct 7 mentioned later is provided in the back panel 1c and the base part 1d.

As shown in FIG. 11, the upper part in the housing 1 communicates with the said clothes inlet 2, and the drum 4 for accommodating the clothes C as a drying object is rotatably supported. When the lid 3 is opened, the clothes C can be accommodated in the drum 4 through the clothes inlet 2.

The drum 4 has a bottomed cylindrical shape having a center of rotation along the horizontal direction in the front and rear directions, and the central portion of the bottom portion is in the side wall portion of the rear panel 1c with the opening facing the clothes inlet 2. It is rotatably supported by the shaft 30, and this drum 4 is made to rotate about a rotation axis center (refer FIG. 13).

The shaft 30 is connected to a drum rotation motor (not shown) disposed in the housing 1, and when the clothes dryer D operates, the shaft 4 is driven by the drum rotation motor. It is made to rotate at a predetermined speed. Further, the drum 4 may be rotated directly by a belt (not shown) by the rotating motor.

The drum 4 has an air outlet 31 for discharging the drying air used for drying the clothes C, and an air inlet 32 through which the drying air used for drying the clothes C is introduced. In communication. A circulation duct 8 for circulating drying air is connected to the air discharge port 31 and the air inlet port 32, and the circulation ventilation path (B) is formed by the space in the circulation duct 8 and the drum 4. 8a) is configured.

The circulation duct 8 includes the air passage side duct 5 whose one end communicates with the air outlet 31, a blower duct 7 whose one end communicates with the air inlet 32, the air passage duct 5 and It is comprised by the heat-drying duct 6 which connects the other ends of the ventilation duct 7. Moreover, the fluff filter 29 is provided between the

ducts

5 and 6, and it collect | acquires the fluff which generate | occur | produced from the clothing C, and can take out to the outside as needed.

More specifically, the path side duct 5 is formed so that the front side in the housing 1 may extend along an up-down direction, and the upper end part is connected to the air discharge port 31 in airtight state. The heat-drying duct 6 extends along the front-back direction in the bottom part side inside the housing 1, and the front end part is connected to the lower end part of the channel side duct 5 in airtight state. The blowing duct 7 is formed so that it may extend up and down along the rear panel 1c of the housing 1, The lower end part is the rear end part of the heating and drying duct 6 via the fan casing 10b mentioned later. The upper end portion is connected to the rear panel 1c in an airtight state while being connected to the airtight state. As shown in FIG. 13, the said air inlet 32 is provided with the round hole part 32a which consists of many round hole which penetrates in the front-back direction, and it drys through this round hole part 32a. Air flows into the drum 4 from the blowing duct 7 (see arrow A3). The outer circumferential portion of the rear panel 1c and the air inlet 32 is rotatable by the hermetic chamber 75 and is connected in the hermetic state.

Returning to FIG. 11, in the circulation ventilation path 8a, the evaporator 9a which consists of a heat exchanger as a cooling apparatus which cools and dehumidifies air, and the same condenser 9b as a heating apparatus which heats the air which passed this cooling apparatus are heated. ) Is installed. The evaporator 9a is arrange | positioned at the upstream side (front side) of the circulation ventilation path 8a, and the condenser 9b is arrange | positioned at the downstream side (rear side) of the evaporator 9a at predetermined intervals. . Moreover, the clothes dryer D is equipped with the compressor and the decompression device which are not shown in the housing 1, This compressor and the decompression device are connected to the evaporator 9a and the condenser 9b in piping, respectively, and a heat pump cycle It consists of:

Under the heat-drying duct 6, an accommodating dish portion 11 for collecting and storing the condensed water W generated in the evaporator 9a is provided. The housing plate 11 is opened upward, and the opening of the housing plate 11 is closed by the cover base 6a, whereby the heating and drying duct 6 and the housing plate 11 are formed. ) Is partitioned.

The cover base 6a is provided with a drain hole 6b as a communication path penetrating in the up and down direction immediately below the evaporator 9a, for drying in the circulation ventilation path 8a in the evaporator 9a. The condensed water W generated when the air is dehumidified is discharged to the receiving dish portion 11 through the drain hole 6b. Here, the cover base 6a is inclined downwardly as it approaches the drain hole 6b at the lower side of the evaporator 9a, and drains the condensed water W dropped around the drain hole 6b. It is led to the hole 6b.

The storage dish portion 11 recovers the condensed water W through the drain hole 6b. Here, the bottom face 11a of the accommodating dish part 11 is inclined downward as it goes back, and the recovered condensed water W flows back. And the communication channel 14 is integrally connected to the rear end part of the accommodating dish part 11, and the condensed water W which flowed from the said communication channel 14 to the rear end side of this communication channel 14 is carried out. The pump chamber 16 which accommodates this is integrally connected.

In the pump chamber 16, the pump 19 which sends condensed water, and the water level sensor 21 which detects the water level in the pump chamber 16 are arrange | positioned. A suction hose 20 is connected to the discharge port of the pump 19, and the other end of the suction hose 20 is connected to a separate storage tank 25, and condensed water W pumped up from the pump chamber 16. ) Is fed into the water storage tank 25.

The water storage tank 25 is provided in the storage dish part 26 for water storage tanks of an accommodating dish shape, and the condensed water W which overflowed from the storage tank 25 is stored in the storage dish part 26 for water storage tanks. It is supposed to accept. One end of the water leakage prevention hose 24 is connected to the bottom of the reservoir plate 26 for the storage tank. The other end of the water leakage prevention hose 24 is connected to the pump chamber 16 so that the condensed water W overflowing from the reservoir tank 25 is returned to the pump chamber 16 through the water leakage prevention hose 24. It is.

(Configuration of Fan Unit)

The fan apparatus 10 is provided in the connection part (rear end part of the bottom side in the housing 1) of the heat-drying duct 6 and the ventilation duct 7. Specifically, as shown in FIG. 11 and FIG. 12, the fan apparatus 10 is rotatably supported in the fan casing 10b and the fan casing 10b and has a cylinder having a plurality of blades in the side surface portion. The impeller 10a of the shape is provided. As the fan device 10, for example, a centrifugal fan device including a multi-fan (sirocco fan) can be applied.

As shown in FIG. 16, the fan casing 10b is comprised so that the outer side of the impeller 10a may be covered, and it is provided continuously and integrally with the base cover part 10c and the base cover part 10c, and the said base The connection cover part 10d comprised so that it may extend toward the upper side from the left side of the cover part 10c is provided. The rear surface of the base cover part 10c and the connection cover part 10d is opened, and the fan casing 10b is assembled with the outer cover 71 of the ventilation duct 7 mentioned later. In addition, the fan casing 10b and the back panel 1c are connected in the airtight state by the airtight seal 13, and the connection cover part 10d and the base part 1d are airtight by the airtight seal which is not shown in figure. It is connected in a state. Surrounding the impeller 10a by the outer cover 71 and the base cover part 10c in the installed state, and by the outer cover 71 and the connection cover part 10d, A jet port 10f is formed which opens in a direction perpendicular to the rotation axis of the impeller 10a.

On the front face of the base cover part 10c, a circular inlet 10e is formed which opens in a direction parallel to the rotation axis of the impeller 10a, and the inlet 10e is a heating and drying duct ( It is connected in the airtight state to the rear end of 6).

Thereby, the drying air sucked into the fan apparatus 10 from the heat-drying duct 6 via the inlet port 10e is perpendicular | vertical with respect to the rotating shaft of the said impeller 10a by rotation of the impeller 10a. It is made to be sent to the blowing duct 7 through the blowing port 10f in a direction (refer to arrow A3 of FIG. 11 and FIG. 12).

(Configuration of Blowing Duct)

Hereinafter, the structure of the blowing duct 7 is demonstrated in detail.

As shown to FIG. 10 and FIG. 17, the recessed part 72 concave toward the front side is formed in the rear panel 1c, The ventilation duct 7 is the said recessed part 72 and the rear panel ( It is comprised by the outer cover 71 extended in the up-down direction so that the outer panel 1c may be followed by the outer side of 1c.

More specifically, as shown in FIG. 17, the recessed part 72 of the back panel 1c is formed so that the lower end part may connect with the blower outlet 10f of the fan casing 10b, and is rearward from the lower end part. It is concave upward along the panel 1c, and the drying air sent out from the blowing port 10f of the fan casing 10b is directed toward the air inlet 32 of the drum 4. As shown in FIG.

Moreover, in the recessed part 72 of the rear panel 1c, as shown in FIG. 12, in the connection part of the said recessed part 72 and the air inlet 32, the said air inlet 32 A ventilation opening 72b is formed in accordance with the shape. The ventilation opening 72b is opened in an upper ventilation opening 72b1 opened in a shape along the upper edge (downstream side) of the round hole 32a, and in a shape along the right outer edge of the round hole 32a. The right vent 72b2 and the left vent 72b3 opened in the shape along the outer edge of the left side of the round hole part 32a are included. In addition, the shape of the ventilation opening 72b may not be limited to the shape of FIG. 12, For example, the ventilation opening 72b may have four or more openings.

As shown in FIG. 14, the outer cover 71 is concave toward the rear side, and the box-shaped outer cover main body 71a which the front side opens is opened, and the said outer cover 71 is attached to the rear panel ( The connection plate part 71h for attaching to 1c and the base part 1d is provided. The connection plate part 71h extends continuously integrally toward the outward direction along the back panel 1c and the base part 1d from the outer peripheral edge part of the said outer cover main body 71a, and penetrates in the front-back direction 71 g of mounting holes are formed at predetermined intervals over the entire circumferential direction thereof. Moreover, in the connection plate part 71h, the groove part 71i along the said circumferential direction is formed in the inner side of 71 g of installation holes, and the outer cover 71 is provided in the groove part 71i. ), The seal portion 71j is placed between the rear panel 1c and the base portion 1d in an airtight state (see Fig. 15).

The outer cover main body 71a has an air guide configured to guide the drying air fed from the fan apparatus 10 to the blowing duct 7 to the vent hole 72b formed in the recess 72 of the rear panel 1c. 73 is integrally installed. For example, the outer cover 71 is a resin molded product, and the air guide 73 is formed by integral molding with the outer cover 71.

(Configuration of Air Guide)

Hereinafter, the structure of the air guide 73 is demonstrated in detail. In the following description of "Configuration of the air guide", it is assumed that the outer cover 71 and the rear panel 1c are in a connected state.

As shown in FIG. 14, the air guide 73 is integrally provided with the guide part 73a and the guide part 73b provided in the said outer cover main body 71a so that it may protrude toward the front side from the outer cover main body 71a. , 73c).

The guide portion 73a has an upper edge (downstream side) of the vent port 72b formed in the recess 72 of the rear panel 1c, that is, an upper edge of the upper vent port 72b1 of the vent port 72b. The outer cover main body 71a is integrally formed in the shape which follows. Specifically, as shown in FIG. 13 and FIG. 1 A, the guide portion 73a faces the rearward direction (the direction away from the upper edge of the upper vent 72b1), and the lower direction (upstream direction). Has an inclined surface 73e which is inclined so as to face upward. The inclined surface 73e is an arc-shaped curved surface which is concave rearward and upward (direction spaced apart from the circulating ventilation path 8a). In addition, the inclined surface 73e is not limited to the arc-shaped curved surface, For example, the inclined surface 73e may be a plane inclined so that it may face downward.

As shown to FIG. 14 and FIG. 15B, the

guide parts

73b and 73c extend toward the front side from the surface of the outer cover main body 71a, respectively, and fan casings respectively from the both ends of the guide part 73a, respectively. It is formed integrally with the guide portion 73a so as to extend continuously to the connecting portion with the ejection port 10f of 10b). In addition, a space 74 (air layer) is provided between each of the

induction portions

73b and 73c and the side walls in the up, down, left, and right directions of the outer cover body 71a. By providing such a space 74, it is possible to prevent the noise generated in the blower duct 7 from leaking outward through the up, down, left, and right side walls of the blower duct 7. In addition, since the drying air does not directly contact the side walls in the up, down, left and right directions of the outer cover body 71a, the heat of the drying air does not contact the atmosphere through the outer wall, and a heat insulating effect can also be obtained. In addition, although not shown in figure, the heat insulation and sound insulation material is affixed on the back surface (rear end surface) of the outer cover main body 71a over the whole surface.

In addition, as shown in FIG. 18, the lower end part of the

guide parts

73b and 73c and the upper end part 10g of the connection cover part 10d of the fan casing 10b are the said outer cover 71 and the fan casing 10b. In this connected state, it is comprised so that the inner surface (surface on the side of a ventilation path) in each edge part may become the same height. Specifically, the upper end portion 10g of the connection cover portion 10d is configured to be concave outward by the thickness portion (including the margin) of the

induction portions

73b and 73c. The lower end part is connected to the recessed part of the said connection cover part 10d, respectively.

By setting the air guide 73 in such a configuration, the drying air (see arrow A3 in FIG. 13) fed from the fan device 10 to the blowing duct 7 is guided

portions

73b and 73c of the air guide 73. Guides toward the air inlet 32 side, and thereafter flows along the inclined surface 73e of the guide portion 73a, and the vent hole 72b formed in the concave portion 72 of the rear panel 1c, and It is led to the round hole part 32a of the air inlet port 32. As a result, the swirl flow of the drying air is prevented from occurring in the blowing duct 7, and the drying air can be fed into the drum efficiently. That is, the pressure loss in the ventilation path (circulating ventilation path 8a) in the ventilation duct 7 can be reduced.

In addition, when the outer cover 71 and the fan casing 10b are connected, the surface of the inner side of the lower end portions of the

guide parts

73b and 73c (the circulating ventilation path 8a side), and the connection cover part of the fan casing 10b. Since the surface of the inner side (circulation ventilation path 8a side) of the upper end part 10g of 10d is comprised so that it may be flat, the air in the connection part of the connection cover part 10d and the said guidance |

induction part

73b, 73c is Flows smoothly, noise is suppressed and pressure loss can be reduced.

Therefore, the clothes dryer D can improve the performance compared with the conventional structure at the point that drying time, noise reduction, and energy saving can be made compatible at low cost.

Operation of the clothes dryer

Next, the operation | movement operation of the clothes dryer D which concerns on this Embodiment 2 is demonstrated.

First, when the clothes dryer D starts to operate, the drum rotation motor, the fan device 10 and the heat pump system operate. By the operation of the fan device 10, the upstream side (between the fan device 10 and the condenser 9b) of the fan device 10 in the circulation ventilation path 8a becomes negative pressure, while the fan device 10 The downstream side (between the fan apparatus 10 and the air inlet 32) becomes a static pressure, and a pressure difference produces. For example, the air pressure on the upstream side of the fan apparatus 10 may be 300 Pa or more lower than the atmospheric pressure. According to this differential pressure, the air in the drum 4 circulates in the circulation ventilation path 8a.

Specifically, as shown by arrows A1 and A2 in FIG. 11, the air for drying in the drum 4 flows into the channel-side duct 5 through the air outlet 31, and the front side in the housing 1. Flows downward and flows into the heating and drying duct 6.

And as shown by the arrow A2 of FIG. 11, the air which flowed into the heat-drying duct 6 flows downward in the housing 1 toward the rear along this heat-drying duct 6. In the heat drying duct 6, since the evaporator 9a and the condenser 9b of the heat pump system are sequentially disposed toward the downstream side, the drying air is passed through the heat drying duct 6. Accompanying, first, it is cooled and dehumidified in the evaporator 9a, and then heated in the condenser 9b, and adjusted to a state suitable for drying the clothes C.

Since the inlet port 10e and the jet port 10f of the fan apparatus 10 face the duct 6 and the blow duct 7 for heating and drying, respectively, as shown by arrows A2 and A3 of FIG. The drying air which has passed through the drying duct 6 flows in through the fan apparatus 10, and flows into the blowing duct 7 after it is sent out from it. Moreover, as shown by arrow A3 of FIG. 11, after the air for drying which flowed into the blowing duct 7 flows upward through the rear side in the housing 1 along this blowing duct 7, the air inlet port Flow into the drum (4) through (32). The flow of air in the air blowing duct 7 is as described in the above "Configuration of Air Guide", and the detailed description thereof is omitted here.

By repeating the above circulation process, the drying air is maintained at a predetermined humidity and temperature while the clothes dryer D is operating, whereby the clothes C in the drum 4 are dried.

Embodiment 3

Finally, Embodiment 3 will be described based on the drawings. The third embodiment is shown in FIGS. 19 to 37.

(Form A of Embodiment 3)

19 to 22 show a dryer 1 according to the form A of the third embodiment. The dryer 1 includes a housing formed in a substantially rectangular parallelepiped shape that is long in the vertical direction with a front plate 3a, a rear plate 3b, a ceiling plate 3c, a bottom plate 3d, and a pair of side plates 3e and 3f. 3) is provided. The rear plate 3b and the

side plates

3e and 3f may be formed separately and assembled together to form a cross-sectional inverted c shape from the rear, or may be integrally formed in a three-sided cross-sectional inverted c shape from the beginning. In the following description, for convenience of explanation, the right side is referred to as the "right side" and the left side is referred to as the "left side" from the rear plate 3b side toward the front plate 3a side, and the right side of the

side plates

3e and 3f is referred to. 3e and left are 3f. An opening 5 is formed in the front plate 3a to open and close a drying object such as clothing or blanket, and the opening 5 is openable by the door 7. An operation / display section 6 is provided above the inlet 5 of the front plate 3a. In the housing 3, a drum 9, which is formed in a substantially bottomed cylindrical shape with a bottom face 9a and a side face 9b, is rotatably supported so as to open toward the inlet 5 side. . A supply air supply port (not shown) is formed in the bottom portion 9a of the drum 9, and an exhaust port 11 is provided on the opening side of the drum 9. Further, a reinforcing plate 4 shown in FIGS. 24 and 25 is installed on the bottom plate 3d of the housing 3 in front of the drum 9 in an upward direction in the front-rear direction, and the reinforcing plate ( The fastening hole 4a is penetratingly formed in the vicinity of the center part upper end part of 4). Moreover, 3 g of plate-shaped protruding wall parts protrude integrally in the upper end part of the said back board 3b, and the coupling hole 3h is penetratingly formed in the substantially center part of the said protruding wall part 3g. . As shown in FIG. 23, a plurality of locking piece portions 3i protrude from the left side of the protruding wall portion 3g. In addition, as shown in FIG. 27, also in the upper end part of the said

side plate

3e, 3f, the protrusion part 3j protrudes inwardly over the front-back direction, and the upper surface (

side plate

3e, 3f) of the said protrusion part 3j. End face), a plurality of locking portions 3k and a screw hole (not shown) are formed.

One end portion communicates with the air supply port of the bottom portion 9a of the drum 9, and the other end portion communicates with the exhaust port 11 of the drum 9 via the fluff filter 12. The blowing duct 13 is arrange | positioned so that the lower side of the drum 9 may pass. The fluff filter 12 traps the fluff from the object to be dried, such as clothes and sheets, during the drying operation, thereby preventing the attachment of the fluff to the object to be dried. Below the drum 9, as shown in FIG.21 and FIG.22, the air blower 15 which blows air in the air blowing duct 13 toward the air supply of the drum 9, and the compressor which compresses a refrigerant | coolant ( 16) cools the air heated by the condenser 17 and the dehumidifier 17 as a heating device for releasing the heat of the refrigerant compressed by the compressor 16 to heat the air in the blower duct 13. Thereby, the evaporator 19 which removes the water contained in the said air, and the motor 30 which rotationally drives the drum 9 through the drum belt 30a are provided. Below the evaporator 19, a condensate receiver 21 for storing condensate generated in the process of removing water from the air heated by the condenser 17 by the evaporator 19 is provided.

A water storage tank case 23 is disposed at a corner of the right side plate 3e side of the drum 9 in the space S1 between the drum 9 and the top plate 3c of the housing 3. The storage tank 25 is attached to the storage tank case 23 in a detachable manner. The reservoir tank 25 is connected to the condensate receiver 21 via a transfer pipe 27, and a pump 29 is interposed in the vicinity of an end portion below the transfer pipe 27. When the condensed water stored in the condensed water receiver 21 reaches a predetermined amount, the condensed water in the condensed water receiver 21 is transferred to the water storage tank 25 through the transfer pipe 27 by the driving of the pump 29. Since the reservoir tank 25 is detachably attached to the reservoir tank case 23, when the reservoir tank 25 becomes full, the user removes the reservoir tank 25 from the reservoir tank case 23, and the reservoir tank 25. The water in 25 can be discarded.

Around the upper end of the substantially center part of the reinforcement board 4 and the back board 3b of the said housing 3, it is entangled by the elongate reinforcement member 31 extended in the front-back direction, as shown also in FIGS. It is. In addition, in FIG. 20, the shape illustration of the reinforcement member 31 is simplified. The reinforcement member 31 can be comprised, for example with sheet metal, such as a galvanized steel plate (SGCC) and an iron plate. The part except the longitudinal direction both ends of the reinforcing member 31 is an elongated plate-shaped main surface portion 31a extending in the front-rear direction and a side portion 31b projecting downward so as to face each other from left and right sides of the main surface portion 31a. The cross section is formed in an inverted U shape. As shown in FIG. 25, three screw insertion holes 31c are formed in the main surface part 31a at intervals in the longitudinal direction (car body front-back direction). The longitudinal direction both ends of the reinforcing member 31 consist of only the main surface part 31a, and the longitudinal front end part of the main surface part 31a constitutes the contact part 31d projecting downward at a right angle, while the main surface part 31a is formed. The longitudinal rear end of the cross section comprises a coupling portion 31e protruding in a substantially L shape. 31f of fastening holes are formed through the said contact part 31d. By inserting the screw 34 through the fastening hole 31f of the contact part 31d and the fastening hole 4a of the reinforcing plate 4 while the contact part 31d is in contact with the reinforcing plate 4, By engaging the contact portion 31d of the reinforcing member 31 with the reinforcing plate 4 and engaging the engaging portion 31e with the engaging hole 3h of the protruding wall portion 3g of the back plate 3b, The reinforcing member 31 is fixed to the reinforcing plate 4 and the back plate 3b.

26, 28-31, the said blower 15 is shown in the corner part of the side plate 3f side of the left side (one side) in the space S1 between the said drum 9 and the ceiling plate 3c. ), A control circuit unit 32 for controlling the compressor 16 and the motor 30 is disposed. The control circuit unit 32 is provided with the support member 33 which has the inclined surface part 33a of substantially rectangular plate shape, and this support member 33 is the space between the said drum 9 and the ceiling plate 3c. The housing is placed in a corner portion of the side plate 3f on the left side (one side) in (S1), and the inclined surface portion 33a is inclined downward toward the left side plate 3f side (left side). (3) and the reinforcing member 31 are fixed. This support member 33 can be comprised with sheet metal, such as resin and a galvanized steel plate (SGCC), and when comprised with sheet metal, especially high strength and heat resistance are acquired. On the right (inner) end edge of the inclined surface portion 33a, an approximately rectangular plate-shaped fastening surface portion 33b is integrally extended toward the right side substantially horizontally. Three screw insertion holes 33c are formed in this fastening surface part 33b at a position corresponding to the screw insertion hole 31c of the reinforcing member 31, and these screw insertion holes 33c are described above. The fastening surface portion 33b of the support member 33 is fixed to the reinforcing member 31 by corresponding to the screw insertion hole 31c of the reinforcing member 31 and inserting and fastening the screw 35 therebetween. . On the left (outer) end edge of the inclined surface portion 33a, a first vertical surface portion 33d extends substantially upward, and the first vertical surface portion 33d is formed as shown in FIG. 27. A curved concave portion 33e is formed to concave in a concave shape so as to approach the side plate 3f on the left side, and the curved concave portion 33e is formed in the lower space S2 of the protruding portion 3j of the side plate 3f. Is located. A plate-shaped locking surface portion 33f is integrally provided to the left edge of the first vertical surface portion 33d substantially horizontally toward the left side, and a plurality of caught portions 33g are provided on the locking surface portion 33f. And the screw hole 33h is formed so as to correspond to the engaging portion 3k and the screw hole of the protruding portion 3j of the side plate 3f. These held portions 33g are held by the locking portions 3k of the side plates 3f, and are screwed into the screw holes 33h of the locking surface portions 33f and the screw holes of the side plates 3f. ), The engaging surface portion 33f of the support member 33 is fixed to the side plate 3f of the housing 3 by inserting and fastening. Moreover, the 2nd vertical surface part 33i which rises upward also protrudes and is provided also in the rear edge of the inclined surface part 33a of the said support member 33, and a board is provided in the front-end edge of the said 2nd vertical surface part 33i. The installation surface part 33j of the shape is integrally extended and installed substantially horizontally toward the rear. A plurality of locking holes 33k are formed in the mounting surface portion 33j so as to correspond to the locking piece portions 3i of the rear plate 3b, and the locking piece portions of the rear plate 3b are placed in these locking holes 33k. The insertion surface engaging portion 33j of the support member 33 is fixed to the rear plate 3b of the housing 3 by inserting and engaging 3i. In addition, as shown in FIG. 28, the plurality of bulging portions 33m is formed in the supporting member 33. This increases the strength of the support member 33 and prevents its deformation. In addition, detailed illustration of the bulging part 33m etc. is abbreviate | omitted in FIG.26, FIG.27 and FIG.31. 32, two fastening holes 33n are formed in the vicinity of the right end edge of the inclined surface portion 33a of the supporting member 33 at intervals in the front-rear direction, while the inclined surface portion ( In the vicinity of the left end edge of 33a), two rectangular locking holes 33p are formed at intervals in the front-rear direction.

On the surface of the half drum 9 side of the inclined surface part 33a of the said support member 33, as shown in FIG. 29, the rectangular-shaped bottom wall part 39a and the whole of the bottom wall part 39a are shown. The resin circuit case 38 having the case body 39 formed in an approximately low plate shape with an annular circumferential wall portion 39b protruding from the circumference has a half inclined surface portion 33a with the opening side of the case body 39 extended. ) And the longitudinal direction of the case main body 39 in the front-rear direction. On the front side and the rear side surfaces of the circumferential wall portion 39b, a guide portion 39c extending substantially obliquely in the shape of a cross-section and extending downward in a downward direction to the left side is formed in the semi-projection direction of the circumferential wall portion 39b. It protrudes integrally so that 39d of recessed recesses may be formed. Therefore, the recessed groove 39d also extends inclined downward toward the left side. At the left (outer) end of the circumferential wall portion 39b, the engaging portion 39e protrudes back and forth. Moreover, in the vicinity of the front and rear ends of the right side surface of the circumferential wall part 39b, as shown in FIG. 31A and FIG. 31B, the outer fastening part 40 which has the threaded insertion hole 40a protrudes integrally. . Moreover, the inner fastening part 42 which has the screw insertion through-hole 42a protrudes integrally in the circumferential wall part 39b of the inside of the front-back direction rather than these outer fastening parts 40 integrally. In addition, at the left end of the bottom wall portion 39a of the case main body 39, two locking hook portions 46 projecting to the left side are formed at intervals in the front-rear direction. In the state where the hooking hook portion 46 is inserted into the hooking hole 33p of the support member 33 and hanged, the screw insertion hole 42a of the inner fastening portion 42 and the support member ( The circuit case 38 is attached to the support member 33 by inserting and screwing the screw 44 into the fastening hole 33n of 33. In addition, illustration of the outer fastening part 40 and the inner fastening part 42 is abbreviate | omitted in FIG. 29 and FIG.

The circuit case 38 houses a control board 41 for controlling the blower 15, the compressor 16, the pump 29, and the motor 30. The control board 41 controls the load of each part in order to make desired dry state based on the temperature detection result etc. The urethane resin in the molten state is introduced into the circuit case 38 and solidified in the state where the control board 41 is coupled to the hook portion of the bottom wall portion 39a of the circuit case 38. The control board 41 is fixed. In this state, the control board 41 is surrounded by the circumferential wall portion 39b of the circuit case 38.

The resin cover member 43 which covers the said control board 41 from the half inclined surface part 33a side is fixed to the circuit case 38 at intervals between the said control board 41. The cover member 43 is concave to the half bottom wall part 39a side, and the left end part of the cover member 43 is located in the lower space S2 of the protrusion part 3j of the said side plate 3f. The cover member 43 includes an upper wall portion 43a for covering the control board 41 from the half bottom wall portion 39a side, and the upper wall portion (for covering the control board 41 from the front side and the rear side). The upper side wall portion 43b and the rear side wall portion 43c protruding downward from the front edge and the rear edge of 43a, and the upper wall portion so as to cover the control board 41 from the right side (inner side). The inner side wall part 43d which protrudes below from the right (inner side) edge of 43a) is provided. The upper wall portion 43a has a horizontal wall portion 43e extending substantially horizontally with a slight gap between the ceiling plates 3c, and the bottom wall portion (from the left (outer) end edge of the horizontal wall portion 43e). It is provided with the inclined wall part 43f extended inclined downward toward the left side substantially parallel to 39a). A plate-shaped engaging piece 43h is integrally protruded downward from the lower end portions of the front side wall portion 43b and the rear side wall portion 43c, and the coupling piece 43h is the circuit case 38. Is coupled to the recessed groove 39d. The cover member 43 is connected to the upper wall portion 43a in a state in which an opening portion 43g which opens to the left side engages the coupling piece portion 43h with the concave groove 39d of the circuit case 38. The control substrate 41 is formed to pass along the recessed groove 39d to be inserted into and out of the lower space S2 of the protrusion 3j. Further, on the outer (left) end edges of the front side wall portion 43b and the rear side wall portion 43c, a substantially rectangular engaging concave portion 43i concave to the inner side (right side) is formed. The engaging portion 39e of the circuit case 38 engages in the portion 43i to restrict the movement of the cover member 43 toward the half support member 33 and the movement to the left. In addition, an insertion through hole 43j for passing the wiring is formed in the vicinity of the inner side (right side) end portion of the front side wall portion 43b and the rear side wall portion 43c. In addition, illustration of the insertion through hole 43j is abbreviate | omitted in the left figure and the right figure of FIG.

On the inner side wall portion 43d, a fastening portion 45 having a screw insertion through hole 45a is protruded to the inner side (right side), and the fastening portion 45 and the outer fastening portion of the circuit case 38 are provided. The cover member 43 is fixed to the circuit case 38 by making 40 correspond to and inserting and fastening the screw 47 to both screw

insertion holes

40a and 45a. In the inner side wall portion 43d of the fastening portion 45, an upwardly concave, substantially inverted c-shaped cutout 48 is formed so as to correspond to the inner fastening portion 42 of the circuit case 38. In addition, illustration of the fastening part 45 is abbreviate | omitted in FIG.26 and FIG.30.

In order to install the control circuit unit 32 comprised as mentioned above to the housing 3, first, the caught part 33g of the engaging surface part 33f of the support member 33 is caught by the side plate 3f of the left side. It hangs and supports by the part 3k, the fastening surface part 33f of the support member 33 and the protrusion part 3j of the said side plate 3f are fastened with the screw 37, and the fastening surface part of the support member 33 ( 33b) and the reinforcing member 31 are fastened with the screw 35. At this time, an end portion of the control board 41 side of the wiring connecting the blower 15, the compressor 16, the pump 29, the motor 30, and the control board 41 is connected to the support member 33. It draws out on the support member 33 from the clearance gap of the front plate 3a. Thereafter, the circuit case (with the latch hook portion 46 of the circuit case 38 to which the control board 41 is fixed is inserted into the engaging hole 33p of the support member 33 and hanged). The circuit case 38 is supported by inserting and fastening the screw 44 through the screw insertion through hole 42a of the inner fastening portion 42 of the 38 and the fastening hole 33n of the support member 33. The end of the wiring provided on the inclined surface portion 33a of the 33 and drawn out from the gap between the support member 33 and the front plate 3a onto the support member 33, and the operation / display portion 6 and the control board ( The end of the wiring connecting 41 is connected to the control board 41. At this time, since the circuit case 38 is supported by the support member 33 from below, even if a force is applied to the circuit case 38 from the half support member 33 side by the connection work, the support member 33 Without deforming, the circuit case 38 and the control board 41 are hard to be damaged. And wiring is arrange | positioned in the position corresponding to the insertion through hole 43j of the cover member 43, and as shown in the left figure of FIG. 30, the inner side wall part 43d side end part of the said cover member 43 is a circuit. The cover member is spaced apart from the case 38 and from the state in which the engaging recess 43i side end portion of the engaging piece portion 43h of the cover member 43 is coupled to the recessed groove 39d of the circuit case 38. The inner side wall portion 43d side end of the cover member 43 is brought close to the circuit case 38 by sliding 43 outward. At this time, in the process of the cover member 43 slides outward, the control board 41 passes through the opening 43g of the cover member 43 and does not interfere with the cover member 43. Thereby, as shown in the right figure of FIG. 30, a wire penetrates into the insertion through hole 43j of the cover member 43, and the engagement piece part 43h of the cover member 43 is connected to the circuit case 38. As shown in FIG. And the engaging portion 39e of the circuit case 38 to the engaging recess 43i of the cover member 43. In this state, by fastening the fastening portion 45 of the cover member 43 and the outer fastening portion 40 of the circuit case 38 with the screws 47, the cover member 43 is fixed to the circuit case 38. do. Thus, in the lower space S2 of the projection part 3j, even if the left end part of the cover member 43 is not fastened to the circuit case 38 by the engaging part 39e of the circuit case 38, The movement of the cover member 43 to the half support member 33 side and the movement to the left side are restricted. Therefore, the fixing work of the cover member 43 to the circuit case 38 becomes easy, and the number of parts can be reduced as long as a fastening component such as a screw is not used to fasten the left end of the cover member 43.

The cover member 43 fixed as described above covers the cover 47 in a state where the screw 47 is removed and the engaging piece portion 43h of the cover member 43 is coupled to the concave groove 39d of the circuit case 38. By guiding the member 43 to the right side, the member 43 can be taken out from the lower space S2 of the protrusion 3j and removed from the circuit case 38.

Therefore, in the form A of Embodiment 3, since the circuit case 38 is supported by the support member 33 from below, the circuit case 38 at the time of assembling work | work such as the wiring from above, maintenance work, or transportation is carried out. ), Even if a force is applied from the side of the half support member 33, the circuit case 38 and the control board 41 therein are hardly damaged. Therefore, the assembling work, maintenance inspection work, and transportation become easy. In addition, since the support member 33 is interposed between the circuit case 38 and the drum 9, damage to the circuit case 38 and the control board 41 therein due to the contact of the rotating drum 9 is caused. This is avoided.

Therefore, the dryer 1 can improve the reliability compared with the conventional structure at the point that the circuit case 38 and the control board 41 inside it are hard to be damaged.

Moreover, since the supporting member 33 is arrange | positioned at the corner part of one side plate 3f side, it arrange | positions at the center part between both

side plates

3e and 3f in which the space between the drum 9 and the ceiling plate 3c becomes narrow. In comparison with the case, the supporting member 33 can be disposed below. Therefore, the dimension of the control board 41 provided in the half drum 9 side of the inclined surface part 33a can be made high, and the dimension of the control board 41 and the freedom of layout become high. In some cases, even if the control board 41 is enlarged, it is not necessary to divide the control circuit and install it outside the circuit case 38, simplifying the wiring and reducing the influence of noise and the like.

Therefore, the dryer 1 can improve the productivity compared with the conventional structure by the point that the freedom degree of the dimension and layout of the control board 41 becomes high.

Moreover, since the inclined surface part 33a of the support member 33 is inclined downward toward the said one side plate 3f side, compared with the case where it was leveled, the inclined surface part 33a in the vicinity of the said one side plate 3f. ) Can be placed below. Therefore, especially in the vicinity of the said one side plate 3f of the inclined surface part 33a, it becomes possible to raise the dimension of the control board 41 provided in the half drum 9 side of the inclined surface part 33a, The degree of freedom in dimension and layout of the control board 41 is increased.

In addition, since the vicinity of the control board 41 side end of the wiring is pulled out over the support member 33, damage caused by contact with the rotating drum 9 near the control board 41 side end of the wiring is prevented.

Moreover, since the support member 33 is supported from the three directions by the side plate 3f, the back plate 3b of the housing | casing 3, and the reinforcement member 31, fall of the support member 33 by vibration etc. is seen more. It is certainly prevented. In addition, since the strength of the support member 33 is increased at the fixed position with the side plate 3f, the back plate 3b, and the reinforcing member 31, the deformation of the support member 33 due to vibration during transportation or driving, etc. While more reliably prevented, the weight of parts that can be installed on the support member 33 increases, and the degree of freedom of the layout of the control parts arranged in the housing 3 is increased.

In addition, even when water enters the housing 3 from the gap between the side plate 3f and the top plate 3c, the cover member 43 prevents the water from being applied to the control board 41, so that the control board 41 ) Corrosion or short circuit is prevented. In addition, the cover member 43 also prevents the fluff from the object to be dried, such as clothes or sheets, from adhering to the control board 41, thereby preventing the problem of the control board 41 due to the attachment of the fluff.

In addition, since the cover member 43 is fixed to the circuit case 38, the detachment of the cover member 43 due to vibration or the like is prevented.

In addition, since the heat of the control board 41 is released from the opening 43g of the cover member 43, excessive temperature rise of the control board 41 is prevented.

In addition, since the cover member 43 and the circuit case 38 are also disposed in the lower space S2 of the protrusion 3j of the side plate 3f, the cover member 43 and the control board 41 can be enlarged. The degree of freedom of the dimensions and layout of the control board 41 is increased.

In addition, since the cover member 43 has a concave shape toward the half bottom wall portion 39a, and a space is formed inside the cover member 43, the degree of freedom in the dimension and the layout in the height direction of the control board 41 is increased. At the same time, temperature rise due to heat generation of the control board 41 can be alleviated.

In addition, in the form A of Embodiment 3, although the cover member 43 was provided in the circuit case 38 in the state which installed the circuit case 38 in the support member 33, it covers the circuit case 38. The circuit case 38 may be provided on the support member 33 in a state where the member 43 is fixed. In this case, since the installation work of the circuit case 38 and the support member 33 can be performed in the state which protected the control board 41 with the cover member 43, it contacted with the tool etc. at the time of installation work. The problem of the control board 41 due to damage caused by a collision or mixing of foreign matter such as screws can be prevented.

(Form B of Embodiment 3)

33A and 33B show the control circuit unit 32 of the dryer 1 according to the form B of the third embodiment. In the form B of Embodiment 3, the threaded insertion hole 49 is formed in the inclined surface part 33a of the support member 33, and this threaded insertion hole 49 and the threaded insertion of the cover member 43 are penetrated. The cover member 43 is fixed to the support member 33 by inserting and fastening the screws 47 therebetween correspondingly to the holes 45a. On the other hand, the outer case 40 is not provided in the circuit case 38.

Other configurations are the same as those of Embodiment A of Embodiment 3, and therefore, the same components will be denoted by the same reference numerals and detailed description thereof will be omitted.

In Embodiment B of Embodiment 3, since it is not necessary to provide the outer fastening part 40 for fixing the cover member 43 to the circuit case 38, the case main body 39 is enlarged and the control board 41 of the control board 41 is not provided. The storage space can be increased.

(Form C of Embodiment 3)

34A and 34B show the control circuit unit 32 of the dryer 1 according to the form C of the third embodiment. In the form C of Embodiment 3, the threaded insertion hole 49 is formed in the inclined surface part 33a of the support member 33, and this threaded insertion hole 49 and the threaded insertion of the cover member 43 are penetrated. The cover member 43 is connected to the circuit case 38 and the support member 33 by inserting and screwing a common screw 47 into the hole 45a and the screw insertion hole 40a of the circuit case 38. It is fixed to both sides of. The inner fastening portion 42 of the circuit case 38 and the cutout portion 48 of the cover member 43 are not provided.

In the form C of Embodiment 3, compared with the case where the cover member 43 is fixed by only one of the circuit case 38 and the support member 33, separation of the cover member 43 by vibration etc. is prevented more reliably.

(Form D of Embodiment 3)

FIG. 35 shows the circuit case 38 of the dryer 1 according to the form D of the third embodiment. In the form D of Embodiment 3, the circuit case 38 accommodates the control component which is not shown by the reactor etc. which were connected to the control board 41 via wiring at the back side of the said control board 41, have. Between the control component and the control board 41, it is partitioned back and forth by the double plate-shaped partition part 53 which protrudes from the bottom wall part 39a. The control component is covered by the cover member 43 from the half inclined surface portion 33a side.

In the form D of Embodiment 3, since the wiring which connects a control component and the control board 41 does not need to be drawn out of the circuit case 38, wiring operation becomes easy. In addition, even when water enters the housing 3 from the gap between the

side plates

3e and 3f and the ceiling plate 3c, the cover member 43 prevents the water from being applied to the control component. Problems with parts are prevented.

In addition, since the plate-shaped partition 53 prevents the inflow of the urethane resin used for moisture proof (high accuracy) of the control board 41 to the control part side, the detachable control part can be easily attached and detached and urethane The cost is also suppressed by reducing the amount of resin.

(Form E of Embodiment 3)

36 shows the periphery of the control circuit unit 32 of the dryer 1 according to the form E of the third embodiment. In the form E of Embodiment 3, the bending recessed part 33e is not formed in the support member 33, and the whole cover member 43 is located on the right side rather than the lower space S2 of the protrusion part 3j. In addition, the opening part 43g is not formed in the cover member 43.

In the form E of this Embodiment 3, the cover member 43 can be arrange | positioned from a fixed position from upper direction without performing the operation which slides the cover member 43 to the outer side like Embodiments A-D of Embodiment 3. .

(Form F of Embodiment 3)

37 shows the support member 33 of the dryer 1 according to the form F of the third embodiment. In the form F of Embodiment 3, the support member 33 is not provided with the 2nd vertical surface part 33i and the mounting surface part 33j, and is fixed only by the side plate 3f and the reinforcement member 31 of the housing 3. It is.

In the embodiments A to F of the third embodiment, the present invention is applied to the circulation type dryer 1, but the present invention can also be applied to an exhaust type dryer. The blower 15 is not limited to blowing air in the blower duct 13 toward the air supply port of the drum 9, and blows the air heated by the condenser 17 to pass through the drum 9. If it is, for example, it may be blown to discharge the air from the drum (9).

Claims

housing;

An accommodation space installed in the housing and accommodating a drying object;

A circulation ventilation passage through the accommodation space;

A heat pump apparatus having a compressor, a condenser, a throttling mechanism, and an evaporator, connected to form a flow path through which the refrigerant circulates;

An auxiliary heat exchanger provided outside the ventilation path and connected in series with the flow path in the condenser or in parallel with the condenser; And

And cooling means capable of cooling the auxiliary heat exchanger.
The method of claim 1,

And said cooling means comprises a cooling fan device for blowing air outside said housing toward said auxiliary heat exchanger.
The method according to claim 1 or 2,

And the cooling means includes an exhaust fan device which discharges air outside the ventilation path inside the housing to the outside of the housing.
The method of claim 1,

And the compressor may change the compression capacity so that the temperature of the refrigerant discharged from the compressor increases or decreases.
The method of claim 1,

A refrigerant temperature sensor that detects the temperature of the refrigerant discharged from the compressor is installed in the refrigerant pipe connecting the compressor and the condenser.

And said cooling means cools said auxiliary heat exchanger based on a detection result by said refrigerant temperature sensor.
The method of claim 1,

The auxiliary heat exchanger is connected in series with a flow path in the condenser,

The condenser has a first flow path having an upstream end connected to the discharge side of the compressor and a second flow path having a downstream end connected to the throttling mechanism;

A downstream end of the first flow path is connected to an upstream end of the heat dissipation flow path in the auxiliary heat exchanger, while an upstream end of the second flow path is connected to a downstream end of the heat dissipation flow path.
The method of claim 6,

And the condenser is a fin-and-tube type heat exchanger having a plurality of connecting pipe portions connecting one end of each straight pipe portion to each other so as to communicate the plurality of straight pipe portions and the inside of each straight pipe portion with each other.
The method of claim 6,

A bypass flow path for supplying the refrigerant from the downstream end of the first flow path to the upstream end of the second flow path by bypassing the heat dissipation flow path;

And a flow passage selecting means for switching the refrigerant from the downstream end of the first flow passage to flow the heat dissipation flow passage or the bypass flow passage.
The method of claim 1,

The auxiliary heat exchanger is connected in parallel with the condenser,

And a flow path switching means for switching the entire amount of the refrigerant discharged from the compressor to flow through the condenser, or switching a predetermined amount of the refrigerant discharged from the compressor to flow through the auxiliary heat exchanger and the remaining flows through the condenser.
The method of claim 5,

When the auxiliary heat exchanger is connected in parallel to the condenser, the flow rate of the condenser side flowing through the condenser and the flow rate of the auxiliary heat exchanger among the refrigerant discharged from the compressor can be adjusted, while the auxiliary heat exchanger is a flow path in the condenser. In the case of being connected in series with each other, the flow rate distribution means for adjusting a bypass flow rate for bypassing the auxiliary heat exchanger among the refrigerant discharged from the compressor and a flow rate for flowing the auxiliary heat exchanger; And

And control means for controlling the cooling means and the flow rate distribution means based on the detection result by the refrigerant temperature sensor.
The method of claim 10,

And the control means controls the flow rate distribution means such that when the heat pump apparatus starts to operate, the total amount of the refrigerant discharged from the compressor becomes the condenser side flow rate or the bypass flow rate.
The method according to claim 10 or 11, wherein

The control means determines whether or not the coolant temperature exceeds a first temperature set higher than a predetermined target temperature based on a detection result by the coolant temperature sensor, and when it is determined that the first temperature is exceeded. And controlling the flow rate distribution means to reduce the condenser side flow rate or the bypass flow rate by a predetermined amount, and increase the flow rate flowing through the auxiliary heat exchanger by the amount of the decrease amount.
The method of claim 12,

And the control means controls the flow rate distribution means and controls the cooling means to cool the auxiliary heat exchanger.
The method of claim 12,

The control means determines whether or not the refrigerant temperature exceeds the second temperature set higher than the first temperature based on the detection result by the refrigerant temperature sensor, and determines that the second temperature has been exceeded. And the flow rate distribution means for controlling the flow rate distribution means to reduce the condenser side flow rate or the bypass flow rate by a predetermined amount, and increase the flow rate through the auxiliary heat exchanger by the amount of the decrease amount.
The method of claim 12,

On the basis of the detection result by the coolant temperature sensor, the control means determines whether or not the coolant temperature is lower than the third temperature set lower than the target temperature and determines that the coolant temperature is lower than the third temperature. And controlling the flow rate distribution means to reduce the flow rate flowing through the auxiliary heat exchanger by a predetermined amount, and increase the condenser side flow rate or the bypass flow rate by the amount of the decrease amount.
In the control method of the dryer comprising a heat pump device including a compressor and a condenser and an auxiliary heat exchanger connected to the condenser,

Operating the heat pump apparatus;

Flowing the entire amount of the refrigerant to the heat pump apparatus such that the refrigerant discharged from the compressor by the flow distribution means does not flow through the auxiliary heat exchanger;

Detect a first detected temperature of the refrigerant discharged from the compressor by a refrigerant temperature sensor;

Determine whether the first detection temperature exceeds a first temperature set higher than a predetermined target temperature;

And increasing the flow rate of the auxiliary heat exchanger by a predetermined amount when the first detection temperature exceeds the first temperature.
The method of claim 16,

A dryer control method for increasing the flow rate of the auxiliary heat exchanger and cooling the auxiliary heat exchanger by cooling means.
The method of claim 17,

Detect a second detected temperature of the refrigerant discharged from the compressor by the refrigerant temperature sensor;

Determine whether the second detection temperature exceeds a second temperature set higher than the first temperature;

And increasing the flow rate of the auxiliary heat exchanger by a predetermined amount when the second detection temperature exceeds the second temperature.
The method of claim 17,

Detect a second detected temperature of the refrigerant discharged from the compressor by the refrigerant temperature sensor;

Determine whether the second detection temperature is lower than a third temperature set lower than the target temperature;

And the flow rate flowing through the auxiliary heat exchanger is reduced by a predetermined amount when the second detection temperature is less than the third temperature.
The method according to any one of claims 16 to 19,

The condenser is installed inside the circulating air passage through the receiving space for receiving the drying object,

The auxiliary heat exchanger is provided outside the ventilation path, and is connected in series with the flow path in the condenser or in parallel with the condenser,

When the auxiliary heat exchanger is connected in parallel with the condenser, the flow rate distribution means can adjust the flow rate of the condenser side flowing through the condenser and the flow rate flowing through the auxiliary heat exchanger among the refrigerant discharged from the compressor. When the machine is connected in series with the flow path in the condenser, the dryer control method that can adjust the bypass flow rate for bypassing the auxiliary heat exchanger among the refrigerant discharged from the compressor and the flow rate flowing through the auxiliary heat exchanger.