TWI721326B

TWI721326B - Heat exchanger for refrigerating device and refrigerating device

Info

Publication number: TWI721326B
Application number: TW107135920A
Authority: TW
Inventors: 藤野博之; 增野謙
Original assignee: 日商東普雷股份有限公司
Priority date: 2014-02-03
Filing date: 2015-02-03
Publication date: 2021-03-11
Also published as: TWI646293B; JP2018179498A; JP2015163829A; TW201903340A; TW201531658A; JP6420554B2; JP6603768B2

Abstract

本發明的問題在於提供一種冷凍裝置用熱交換器，可以在不使冷卻能力降低的前提下，延長所需的除霜動作的實行間隔。為了解決上述問題，本發明提供一種冷凍裝置用熱交換器，具備：第1熱交換器(3A)，其具有第1冷媒配管線路；第2熱交換器(3B)，其具有串聯連接於第1冷媒配管線路上的第2冷媒配管線路，且與第1熱交換器(3A)並列設置；多個散熱片(3f)，其橫跨連結於第1冷媒配管線路的配管(3cA)與第2冷媒配管線路的配管(3cB)上；及，送風機(FM1)，其對第1熱交換器(3A)和第2熱交換器(3B)送風。多個散熱片(3f)相互平行地相對向並列設置，第1冷媒配管線路的配管(3cA)和第2冷媒配管線路的配管(3cB)，以正交貫穿於多個散熱片的方式連結，第1熱交換器(3A)與第2熱交換器(3B)，以使第1熱交換器(3A)成為送風的上游側的方式並列設置。The problem of the present invention is to provide a heat exchanger for a refrigerating device that can extend the interval between required defrosting operations without reducing the cooling capacity. In order to solve the above-mentioned problems, the present invention provides a heat exchanger for refrigeration equipment, including: a first heat exchanger (3A) having a first refrigerant piping line; and a second heat exchanger (3B) having a series connection to the second heat exchanger 1 The second refrigerant piping line on the refrigerant piping line is arranged in parallel with the first heat exchanger (3A); a plurality of fins (3f) spanning the piping (3cA) connected to the first refrigerant piping line and the first 2 On the piping (3cB) of the refrigerant piping line; and, the blower (FM1), which blows air to the first heat exchanger (3A) and the second heat exchanger (3B). A plurality of radiating fins (3f) are arranged in parallel and facing each other in parallel, and the piping (3cA) of the first refrigerant piping line and the piping (3cB) of the second refrigerant piping line are connected so as to penetrate through the plurality of radiating fins orthogonally. The first heat exchanger (3A) and the second heat exchanger (3B) are arranged side by side so that the first heat exchanger (3A) becomes the upstream side of the blowing air.

Description

冷凍裝置用熱交換器及冷凍裝置Heat exchanger for refrigerating device and refrigerating device

本發明關於一種冷凍裝置用熱交換器及冷凍裝置，尤其關於一種可選擇性地實行冷卻運轉與升溫運轉的冷凍裝置與用於此冷凍裝置的冷凍裝置用熱交換器。The present invention relates to a heat exchanger for a refrigerating device and a refrigerating device, and more particularly to a refrigerating device capable of selectively performing a cooling operation and a temperature increasing operation, and a heat exchanger for the refrigerating device used in the refrigerating device.

作為用於向便利商店等配送商品的冷凍車，載置有以下冷凍裝置的冷凍車得以實際應用，該冷凍裝置由於能夠使裝載於庫內的貨物維持在最佳溫度而不受室外溫度影響，因此，不僅可以將庫內冷卻，還可以升溫。根據該冷凍裝置，庫內當室外溫度高於維持溫度時也就是主要在夏季被冷卻，當室外溫度低於維持溫度時也就是主要在冬季被升溫。在專利文獻1中，作為陸路運輸用冷凍裝置，記載有此冷凍裝置的一例。專利文獻1所述的陸路運輸用冷凍裝置為熱泵式。As a refrigerated car for distributing goods to convenience stores, etc., a refrigerated car equipped with the following refrigerating device has been put into practical use. The refrigerating device can maintain the goods loaded in the warehouse at the optimal temperature without being affected by the outdoor temperature. Therefore, not only can the inside of the library be cooled, but also can be raised. According to this refrigerating device, when the outdoor temperature is higher than the maintenance temperature, it is mainly cooled in summer, and when the outdoor temperature is lower than the maintenance temperature, it is mainly heated in winter. Patent Document 1 describes an example of such a refrigerating device as a refrigerating device for land transportation. The refrigeration device for land transportation described in Patent Document 1 is a heat pump type.

通常，如果冷凍車在降雪時行車，庫外熱交換器由於吹入的雪的附著，會有不能作為升溫運轉的熱交換器而發揮功能的情況。此時，進行除霜(defrost)動作而使附著的雪融解。但是，如果頻繁地實行除霜動作，亦即，如果除霜動作的實行間隔變短，升溫動作的效率將會降低。因此，專利文獻1所述的陸路運輸用冷凍裝置具備以下構造，該構造在冷凍車的降雪時行車中的升溫模式運轉下，防止除霜動作的實行間隔變短。具體來說，具備：風管，其將冷凍車的發動機的排風引導至庫外熱交換器的吸入側；風管內的風路的開關手段；及，面板(Panel)，其以覆蓋庫外熱交換器的方式，配置於庫外熱交換器的吸入側的前方。In general, if a refrigerated vehicle is driving during snowfall, the external heat exchanger may not function as a heat exchanger for heating operation due to the adhesion of the blown snow. At this time, a defrost operation is performed to melt the attached snow. However, if the defrosting action is frequently performed, that is, if the interval between the defrosting actions is shortened, the efficiency of the temperature-raising action will decrease. Therefore, the refrigerating apparatus for land transportation described in Patent Document 1 has a structure that prevents the execution interval of the defrosting operation from shortening during the operation of the temperature-raising mode while the refrigerating vehicle is driving during snowfall. Specifically, it includes: an air duct that guides the exhaust air from the engine of the refrigerated vehicle to the suction side of the external heat exchanger; a means for opening and closing the air passage in the air duct; and a panel (Panel) that covers the warehouse The form of the external heat exchanger is arranged in front of the suction side of the external heat exchanger.

例如，根據面板，雪將不會直接吹入庫外熱交換器。這樣一來，由於積雪得以被抑制而維持作為熱交換器的功能，因此，不再需要縮短除霜動作間隔。For example, according to the panel, snow will not be blown directly into the external heat exchanger. In this way, since snow accumulation is suppressed and the function as a heat exchanger is maintained, it is no longer necessary to shorten the defrosting operation interval.

[先行技術文獻] (專利文獻) 專利文獻1：日本特開2010-255909號公報。[Prior Art Document] (Patent Document) Patent Document 1: Japanese Patent Application Laid-Open No. 2010-255909.

[發明所欲解決的問題] 但是，專利文獻1所述的冷凍裝置，由於面板以覆蓋庫外熱交換器的方式，被配置於庫外熱交換器的吸入側的前方，因此，冷凍車行車時的行車風(車輛行進所產生的風，基於車輛與空氣的相對速度)被面板遮擋，而不能直接吹到庫外熱交換器上。因此，在庫外熱交換器作為冷凝器而發揮作用的冷卻運轉中，可能會產生無法確保充分風量的情況。如果無法確保充分的風量，將會產生以下問題：冷媒不能充分地冷凝，冷卻能力降低。因此，對於冷凍裝置用熱交換器及冷凍裝置，較理想的是，可以在不使冷卻能力降低的前提下，延長所需的除霜動作的實行間隔。[Problems to be Solved by the Invention] However, in the refrigerating device described in Patent Document 1, since the panel is arranged in front of the suction side of the external heat exchanger so as to cover the external heat exchanger, the refrigerated vehicle runs When the driving wind (wind generated by the vehicle traveling, based on the relative speed of the vehicle and the air) is blocked by the panel, it cannot be directly blown to the external heat exchanger. Therefore, in the cooling operation in which the external heat exchanger functions as a condenser, it may not be possible to ensure a sufficient air volume. If a sufficient air volume cannot be ensured, the following problems will occur: the refrigerant cannot be sufficiently condensed, and the cooling capacity is reduced. Therefore, for the heat exchanger for refrigeration equipment and the refrigeration equipment, it is desirable that the interval between the required defrosting operations can be extended without reducing the cooling capacity.

因此，本發明所欲解決的問題在於提供一種冷凍裝置用熱交換器及使用該冷凍裝置用熱交換器的冷凍裝置，該冷凍裝置用熱交換器可以在不使冷卻能力降低的前提下，延長所需的除霜動作的實行間隔。Therefore, the problem to be solved by the present invention is to provide a heat exchanger for a refrigeration device and a refrigeration device using the heat exchanger for a refrigeration device. The heat exchanger for a refrigeration device can extend without reducing the cooling capacity. The interval between the required defrost actions.

[解決問題的技術手段] 為了解決上述問題，本發明具有以下的構成。 (1) 一種冷凍裝置用熱交換器，具備：第1熱交換器，其具有第1冷媒配管線路；第2熱交換器，其具有串聯連接於前述第1冷媒配管線路上的第2冷媒配管線路，且與前述第1熱交換器並列設置；多個散熱片，其橫跨連結於前述第1冷媒配管線路的配管與前述第2冷媒配管線路的配管兩方上；及，送風機，其對前述第1熱交換器和前述第2熱交換器送風；並且，前述多個散熱片相互平行地相對向並列設置，前述第1冷媒配管線路的配管和前述第2冷媒配管線路的配管，以正交貫穿於前述多個散熱片的方式連結，前述第1熱交換器與前述第2熱交換器，以使前述第1熱交換器成為由前述送風機所產生的送風的上游側的方式並列設置。 (2) 如(1)所述的冷凍裝置用熱交換器，其中，前述第1冷媒配管線路具有二個以上的路徑，路徑數為Na（Na：2以上的整數）。 (3) 如(2)所述的冷凍裝置用熱交換器，其中，前述第2冷媒配管線路具有二個以上的路徑，路徑數為Nb（Nb：2以上的整數），前述路徑數Na與前述路徑數Nb，滿足2≤Na≤Nb。 (4) 如(1)～(3)中任一項所述的冷凍裝置用熱交換器，其中，使前述第1熱交換器和前述第2熱交換器中的至少一方為鰭管式熱交換器。 (5) 如(1)～(3)中任一項所述的冷凍裝置用熱交換器，其中，當作為冷凍裝置的前述庫外熱交換器使用時，該冷凍裝置具備包括庫內熱交換器和庫外熱交換器的冷媒回路，且選擇性地進行使庫內冷卻的冷卻運轉與使庫內升溫的升溫運轉，在前述冷卻運轉中，前述第1熱交換器與前述第2熱交換器作為冷凝器而一體地發揮功能，在前述升溫運轉中，前述第1熱交換器作為過冷器而發揮功能，且前述第2熱交換器作為蒸發器而發揮功能。 (6) 如(4)所述的冷凍裝置用熱交換器，其中，當作為冷凍裝置的前述庫外熱交換器使用時，該冷凍裝置具備包括庫內熱交換器和庫外熱交換器的冷媒回路，且選擇性地進行使庫內冷卻的冷卻運轉與使庫內升溫的升溫運轉，在前述冷卻運轉中，前述第1熱交換器與前述第2熱交換器作為冷凝器而一體地發揮功能，在前述升溫運轉中，前述第1熱交換器作為過冷器而發揮功能，且前述第2熱交換器作為蒸發器而發揮功能。 (7) 一種冷凍裝置，具備冷媒回路，該冷媒回路包括庫內熱交換器、庫外熱交換器及可以滯留冷媒的受液器，且該冷凍裝置選擇性地進行使庫內冷卻的冷卻運轉與使庫內升溫的升溫運轉，該冷凍裝置的特徵在於：前述庫外熱交換器是(1)所述的冷凍裝置用熱交換器，在前述冷卻運轉中，前述第1熱交換器與前述第2熱交換器作為冷凝器而一體地發揮功能，在前述升溫運轉中，前述第1熱交換器作為過冷器發揮功能，且前述第2熱交換器作為蒸發器而發揮功能，前述第1熱交換器具有配管列群，該配管列群是將特定容量的一列配管線路在前述送風的方向上串聯地並列設置M（M：1以上的整數）個而成，並且前述M是使前述第1熱交換器的容量為不超過前述受液器的容量的範圍時的最大值。 (8) 如(7)所述的冷凍裝置，其中，前述第1冷媒配管線路具有二個以上路徑，路徑數為Na（Na：2以上的整數），前述配管列群分別與前述二個以上的路徑相對應地設置。[Technical Means for Solving the Problems] In order to solve the above-mentioned problems, the present invention has the following configuration. (1) A heat exchanger for refrigeration equipment, comprising: a first heat exchanger having a first refrigerant piping line; a second heat exchanger having a second refrigerant piping connected in series to the first refrigerant piping line Line, and arranged in parallel with the first heat exchanger; a plurality of radiating fins, which straddle both the piping connected to the first refrigerant piping line and the piping of the second refrigerant piping line; and, the blower, which is opposite The first heat exchanger and the second heat exchanger blow air; and the plurality of radiating fins are arranged in parallel and opposed to each other in parallel, and the piping of the first refrigerant piping line and the piping of the second refrigerant piping line are aligned The first heat exchanger and the second heat exchanger are connected so as to pass through the plurality of radiating fins, and the first heat exchanger and the second heat exchanger are arranged in parallel so that the first heat exchanger becomes the upstream side of the blowing air generated by the blower. (2) The heat exchanger for a refrigeration apparatus according to (1), wherein the first refrigerant piping line has two or more paths, and the number of paths is Na (Na: an integer greater than or equal to 2). (3) The heat exchanger for a refrigeration system according to (2), wherein the second refrigerant piping line has two or more paths, the number of paths is Nb (Nb: an integer greater than or equal to 2), and the number of paths Na is equal to The aforementioned number of paths Nb satisfies 2≤Na≤Nb. (4) The heat exchanger for a refrigeration device according to any one of (1) to (3), wherein at least one of the first heat exchanger and the second heat exchanger is a fin-tube heat exchanger Switch. (5) The heat exchanger for a refrigerating device according to any one of (1) to (3), wherein when used as the aforementioned external heat exchanger of a refrigerating device, the refrigerating device includes an internal heat exchanger. And the refrigerant circuit of the external heat exchanger, and selectively perform a cooling operation to cool the interior and a temperature increase operation to raise the temperature in the interior. In the cooling operation, the first heat exchanger and the second heat exchanger It functions as a condenser integrally, and in the temperature raising operation, the first heat exchanger functions as a subcooler, and the second heat exchanger functions as an evaporator. (6) The heat exchanger for a refrigerating device as described in (4), wherein when used as the aforementioned external heat exchanger of a refrigerating device, the refrigerating device includes a refrigerant including an internal heat exchanger and an external heat exchanger In the cooling operation, the first heat exchanger and the second heat exchanger function integrally as condensers, and the cooling operation to cool the interior and the temperature increase operation to raise the temperature in the interior are selectively performed. In the heating operation, the first heat exchanger functions as a subcooler, and the second heat exchanger functions as an evaporator. (7) A refrigerating device including a refrigerant circuit including an internal heat exchanger, an external heat exchanger, and a receiver capable of retaining refrigerant, and the refrigerating device selectively performs a cooling operation and a cooling system for cooling the inside of the refrigerator. A temperature-rising operation for increasing the temperature inside the refrigerator, characterized in that the external heat exchanger is the heat exchanger for the refrigerator described in (1), and in the cooling operation, the first heat exchanger and the second 2 The heat exchanger functions as a condenser integrally. In the temperature increase operation, the first heat exchanger functions as a subcooler, and the second heat exchanger functions as an evaporator. The first heat The exchanger has a piping row group. The piping row group is formed by arranging M (M: an integer greater than or equal to 1) in series in a row of piping lines of a specific capacity in the direction of the aforementioned air supply, and the aforementioned M is the aforementioned first The capacity of the heat exchanger is the maximum value that does not exceed the range of the capacity of the aforementioned liquid receiver. (8) The refrigeration system according to (7), wherein the first refrigerant piping line has two or more paths, the number of paths is Na (Na: an integer greater than or equal to 2), and the group of piping rows is the same as the two or more paths. Set the path correspondingly.

(發明的效果) 根據本發明，獲得以下效果：可以在不使冷卻能力降低的前提下，延長所需的除霜動作的實行間隔。(Effects of the Invention) According to the present invention, it is possible to obtain the following effect: it is possible to extend the execution interval of the required defrosting operation without reducing the cooling capacity.

根據實施例的庫外熱交換器3、使用此庫外熱交換器3的冷凍裝置51、及它們的變化例，參照第1圖～第19圖，說明本發明的實施形態的冷凍裝置用熱交換器及冷凍裝置。According to the external heat exchanger 3 of the embodiment, the refrigerating device 51 using the external heat exchanger 3, and their modified examples, referring to Figs. 1 to 19, the refrigerating device heat for the embodiment of the present invention will be described. Exchanger and refrigeration unit.

[實施例][Example]

冷凍裝置51的構成，表示於作為此冷媒回路圖的第1圖和表示控制系統的第2圖中。亦即，冷凍裝置51的冷媒回路具有以下構成：壓縮機1、四通閥2、包含由馬達驅動的送風機也就是風扇FM1的庫外熱交換器3、受液器4、包括由馬達驅動的送風機也就是風扇FM2的庫內熱交換器5、蓄液器6、電磁閥11及電磁閥13。The configuration of the refrigerating device 51 is shown in Fig. 1 as the refrigerant circuit diagram and Fig. 2 showing the control system. That is, the refrigerant circuit of the refrigeration device 51 has the following configuration: a compressor 1, a four-way valve 2, an outdoor heat exchanger 3 including a fan FM1 driven by a motor, a receiver 4, and a motor driven The blower is the internal heat exchanger 5, the accumulator 6, the solenoid valve 11, and the solenoid valve 13 of the fan FM2.

冷媒回路中的壓縮機1、四通閥2、風扇FM1、風扇FM2、電磁閥11及電磁閥13的動作，是由控制部31控制。由使用者所作出的關於運轉的指示，經由輸入部32傳達至控制部31。The operations of the compressor 1, the four-way valve 2, the fan FM1, the fan FM2, the solenoid valve 11, and the solenoid valve 13 in the refrigerant circuit are controlled by the control unit 31. The operation instructions given by the user are transmitted to the control unit 31 via the input unit 32.

庫外熱交換器3和庫內熱交換器5是所謂的鰭管式(Fin and Tube)熱交換器。並且，庫外熱交換器3具有以下構成：第1庫外熱交換器3A和第2庫外熱交換器3B；及，將第1庫外熱交換器3A與第2庫外熱交換器3B在冷媒回路上串聯地連接的回路（並聯回路LP1）。第1庫外熱交換器3A具有冷媒配管線路3LA，該冷媒配管線路3LA將埠(port)3Aa與埠3Ab連接（參照第4圖和第7圖）。並且，第2庫外熱交換器3B具有冷媒配管線路3LB，該冷媒配管線路3LB將埠3Ba與埠3Bb連接（參照第4圖和第7圖）。關於此庫外熱交換器3的詳情，於下文中詳述。The external heat exchanger 3 and the internal heat exchanger 5 are so-called fin and tube heat exchangers. In addition, the external heat exchanger 3 has the following configuration: a first external heat exchanger 3A and a second external heat exchanger 3B; and, the first external heat exchanger 3A and the second external heat exchanger 3B A circuit connected in series on the refrigerant circuit (parallel circuit LP1). The first external heat exchanger 3A has a refrigerant piping line 3LA that connects a port (port) 3Aa and a port 3Ab (refer to FIGS. 4 and 7). In addition, the second external heat exchanger 3B has a refrigerant piping line 3LB that connects the port 3Ba and the port 3Bb (refer to FIGS. 4 and 7). The details of this external heat exchanger 3 will be described in detail below.

針對冷凍裝置51的冷媒回路，作詳細敘述。壓縮機1與四通閥2的埠2a，由配管線路L1連接。四通閥2的埠2b與庫外熱交換器3中的第2庫外熱交換器3B的埠3Ba，由配管線路L2連接。第2庫外熱交換器3B的埠3Bb與第1庫外熱交換器3A的埠3Ab，經由並聯回路LP1連接。The refrigerant circuit of the refrigeration device 51 will be described in detail. The port 2a of the compressor 1 and the four-way valve 2 is connected by a piping line L1. The port 2b of the four-way valve 2 and the port 3Ba of the second external heat exchanger 3B in the external heat exchanger 3 are connected by a piping line L2. The port 3Bb of the second external heat exchanger 3B and the port 3Ab of the first external heat exchanger 3A are connected via the parallel circuit LP1.

並聯回路LP1具有以下構成：配管線路L3和配管線路L4。在配管線路L3上配設有：膨脹閥7；及，止回閥8，相對於膨脹閥7串聯連接於第1庫外熱交換器3A側，只允許從第1庫外熱交換器3A朝向第2庫外熱交換器3B流通。在配管線路L4上配設有止回閥9，該止回閥9只允許從第2庫外熱交換器3B朝向第1庫外熱交換器3A流通。The parallel circuit LP1 has the following configuration: a piping line L3 and a piping line L4. The piping line L3 is equipped with an expansion valve 7; and a check valve 8, which is connected in series to the expansion valve 7 on the side of the first external heat exchanger 3A, and is only allowed to go from the first external heat exchanger 3A The second external heat exchanger 3B circulates. The piping line L4 is provided with a check valve 9 which allows only the flow from the second external heat exchanger 3B to the first external heat exchanger 3A.

第1庫外熱交換器3A的埠3Aa與受液器4，由配管線路L5連接。在配管線路L5上，中途設置有分歧部D1和分歧部D2。在分歧部D1與分歧部D2之間，配設有止回閥10，該止回閥10只允許從第1庫外熱交換器3A朝向受液器4流通。The port 3Aa of the first external heat exchanger 3A and the receiver 4 are connected by a piping line L5. On the piping line L5, a branch D1 and a branch D2 are provided in the middle. Between the branch portion D1 and the branch portion D2, a check valve 10 is arranged, and this check valve 10 allows only the flow from the first external heat exchanger 3A to the receiver 4.

受液器4與庫內熱交換器5，經由並聯回路LP2而連接。並聯回路LP2具有以下構成：配管線路L6和配管線路L7。在配管線路L6上配設有：電磁閥11；及，膨脹閥12，相對於電磁閥11串聯連接於庫內熱交換器5側。在配管線路L7上配設有電磁閥13。The receiver 4 and the internal heat exchanger 5 are connected via a parallel circuit LP2. The parallel circuit LP2 has the following configuration: a piping line L6 and a piping line L7. The piping line L6 is provided with an electromagnetic valve 11 and an expansion valve 12 connected in series to the electromagnetic valve 11 on the side of the internal heat exchanger 5. A solenoid valve 13 is arranged on the piping line L7.

庫內熱交換器5與四通閥2的埠2d，由配管線路L8連接。在配管線路L8上，中途設置有分歧部D3和分歧部D4。在分歧部D3與分歧部D4之間，配設有止回閥14，該止回閥14只允許從庫內熱交換器5朝向四通閥2流通。The internal heat exchanger 5 and the port 2d of the four-way valve 2 are connected by a piping line L8. On the piping line L8, a branch D3 and a branch D4 are provided in the middle. Between the branch portion D3 and the branch portion D4, a check valve 14 is arranged, and the check valve 14 only allows the flow from the internal heat exchanger 5 to the four-way valve 2.

配管線路L8中的分歧部D3與配管線路L5中的分歧部D1，由配管線路L9連接。在配管線路L9上配設有止回閥15，該止回閥15只允許從分歧部D3朝向分歧部D1流通。配管線路L8中的分歧部D4與配管線路L5中的分歧部D2，由配管線路L10連接。在配管線路L10上配設有止回閥16，該止回閥16只允許從分歧部D4朝向分歧部D2流通。四個分歧部與四個止回閥也就是分歧部D1～D4、止回閥10及止回閥14～16，構成流通方向限制部RK。流通方向限制部RK，對應於隨著切換四通閥2而進行的流路選擇，對進出於庫外熱交換器3的埠3Aa的冷媒的流通方向進行限制。詳情如下文所述。The branch D3 in the piping line L8 and the branch D1 in the piping line L5 are connected by the piping line L9. A check valve 15 is provided on the piping line L9, and this check valve 15 allows only the flow from the branch portion D3 to the branch portion D1. The branch D4 in the piping line L8 and the branch D2 in the piping line L5 are connected by the piping line L10. A check valve 16 is provided on the piping line L10, and this check valve 16 allows only the flow from the branch portion D4 to the branch portion D2. The four branch portions and the four check valves, that is, the branch portions D1 to D4, the check valve 10, and the check valves 14 to 16, constitute the flow direction restricting portion RK. The flow direction restricting portion RK corresponds to the flow path selection performed with the switching of the four-way valve 2 and restricts the flow direction of the refrigerant that enters and exits the port 3Aa of the external heat exchanger 3. The details are described below.

四通閥2的埠2c與壓縮機1，經由蓄液器6，由配管線路L11連接。The port 2c of the four-way valve 2 and the compressor 1 are connected via a piping line L11 via an accumulator 6.

對於此冷媒回路，控制部31選擇性地控制，使四通閥2的動作成為模式A與模式B中的任一種。參照第3圖具體地進行說明，模式A為以下模式：將埠2a與埠2b連接，並且將埠2c與埠2d連接。模式B為以下模式：將埠2a與埠2d連接，並且將埠2b與埠2c連接。根據四通閥2，在模式A中，選擇流路RA作為冷媒流通的線路（參照第9圖的粗線線路）。並且，在模式B中，選擇流路RB（參照第10圖的粗線線路）。亦即，四通閥2在冷媒回路中，作為選擇冷媒流通的流路的流路選擇部而發揮功能。並且，控制部31控制電磁閥11與電磁閥13，使它們交替地打開。此控制與四通閥2的動作聯動實行。具體來說，如第3圖所示，在模式A中，將電磁閥11打開，且將電磁閥13關閉。在模式B中，將電磁閥11關閉，且將電磁閥13打開。For this refrigerant circuit, the control unit 31 selectively controls so that the operation of the four-way valve 2 becomes either mode A or mode B. For specific description with reference to Fig. 3, the mode A is the following mode: the port 2a and the port 2b are connected, and the port 2c and the port 2d are connected. Mode B is the following mode: connect port 2a to port 2d, and connect port 2b to port 2c. According to the four-way valve 2, in the mode A, the flow path RA is selected as the line through which the refrigerant flows (refer to the thick line in FIG. 9). Also, in the mode B, the flow path RB is selected (refer to the thick line in FIG. 10). That is, the four-way valve 2 functions as a flow path selection unit that selects a flow path through which the refrigerant flows in the refrigerant circuit. In addition, the control unit 31 controls the solenoid valve 11 and the solenoid valve 13 to alternately open them. This control is carried out in conjunction with the action of the four-way valve 2. Specifically, as shown in FIG. 3, in mode A, the solenoid valve 11 is opened and the solenoid valve 13 is closed. In mode B, the solenoid valve 11 is closed, and the solenoid valve 13 is opened.

接著，關於庫外熱交換器3的詳情，參照第4圖～第7圖進行說明。第4圖是與庫外熱交換器3的橫剖面相對應的示意性構成圖。第5圖是從庫外熱交換器3的左斜下方觀察而得的外觀立體圖，第6圖是從右斜下方觀察而得的外觀立體圖。第7圖是用以說明庫外熱交換器3的內部的路徑（冷媒配管線路3LA、3LB）的圖。第4圖～第6圖所示的上下左右前後的各方向，是為了容易理解而適當設定的方向，並不限定設置樣態等。Next, the details of the external heat exchanger 3 will be described with reference to FIGS. 4 to 7. FIG. 4 is a schematic configuration diagram corresponding to the cross section of the external heat exchanger 3. Fig. 5 is an external perspective view of the external heat exchanger 3 viewed obliquely from the lower left, and Fig. 6 is an external perspective view of the external heat exchanger 3 viewed obliquely from the lower right. FIG. 7 is a diagram for explaining the internal paths (refrigerant piping lines 3LA, 3LB) of the external heat exchanger 3. The directions of up, down, left, and right, front and back shown in Figs. 4 to 6 are directions set appropriately for easy understanding, and the installation aspect and the like are not limited.

如上所述，庫外熱交換器3以鰭管式熱交換器的形式而構成。如第4圖所示，作為管路的管3c，在橫剖面上，在前後方向上為4列，在上下方向上各列為14段。亦即，如果是M列N段的鰭管式熱交換器，則M＝4，N＝14。各管3c在左右兩端部處折回地配設，以便像第4圖的粗線所示那樣地連結。As described above, the external heat exchanger 3 is configured in the form of a fin-tube heat exchanger. As shown in FIG. 4, the pipe 3c as a pipeline has 4 rows in the front-rear direction in the cross section, and 14 stages in each row in the up-down direction. That is, if it is a fin-tube heat exchanger with M rows and N stages, M=4 and N=14. The tubes 3c are arranged folded back at the left and right ends so as to be connected as shown by the thick lines in FIG. 4.

4列之中，最前方側的1列包含於第1庫外熱交換器3A中，從後方側算起的3列包含於第2庫外熱交換器3B中。亦即，第1庫外熱交換器3A為1列14段，第2庫外熱交換器3B為3列14段。此處，將1列或串聯連接而成的二個以上的列，作為配管列群G。1列的情況下，為了方便也稱為「配管列群」。因此，第1庫外熱交換器3A具有M＝1的1列配管列群GA，第2庫外熱交換器3B具有M＝3的3列配管列群GB。並且，在第1庫外熱交換器3A中，上方側的7段份的管3cA作為一個冷媒配管線路而構成路徑P1，下側的7段份作為一個冷媒配管線路而構成路徑P2。在第2庫外熱交換器3B中，上方側的各列5段或4段共14根份的管3cB作為一個冷媒配管線路而構成路徑P3，中央部的各列5段或4段共14根份的管3cB作為一個冷媒配管線路而構成路徑P4，下方側的各列5段或4段共14根份的管3cB作為一個冷媒配管線路而構成路徑P5。因此，如第4圖所示，在第1庫外熱交換器3A中，與路徑P1和路徑P2分別相對應地設置有配管列群GA1和配管列群GA2。並且，在第2庫外熱交換器3B中，與路徑P3～P5分別相對應地設置有配管列群GB3～GB5。Among the four rows, one row on the frontmost side is included in the first external heat exchanger 3A, and three rows from the rear side are included in the second external heat exchanger 3B. That is, the first external heat exchanger 3A has 1 row and 14 stages, and the second external heat exchanger 3B has 3 rows and 14 stages. Here, one row or two or more rows connected in series are referred to as the piping row group G. In the case of one row, it is also called "piping row group" for convenience. Therefore, the first external heat exchanger 3A has a piping row group GA with M=1, and the second external heat exchanger 3B has a piping row group GB with M=3. In addition, in the first external heat exchanger 3A, the 7-stage pipe 3cA on the upper side constitutes a path P1 as one refrigerant piping line, and the 7-stage lower pipe constitutes a path P2 as a refrigerant piping line. In the second external heat exchanger 3B, a total of 14 pipes 3cB in 5 or 4 rows in each row on the upper side constitute a path P3 as a refrigerant piping line, and a total of 14 pipes 3cB in 5 or 4 rows in the center portion The root pipe 3cB constitutes the path P4 as one refrigerant piping line, and the 14 pipes 3cB in 5 or 4 steps in each row on the lower side constitutes the path P5 as one refrigerant piping line. Therefore, as shown in FIG. 4, in the first external heat exchanger 3A, the piping row group GA1 and the piping row group GA2 are provided corresponding to the path P1 and the path P2, respectively. In addition, in the second external heat exchanger 3B, piping row groups GB3 to GB5 are provided corresponding to the paths P3 to P5, respectively.

第1庫外熱交換器3A的路徑數Na是2以上的整數，且為第2庫外熱交換器的路徑數Nb（Nb：2以上的整數）以下。亦即，2≤Na≤Nb。冷凍裝置51的庫外熱交換器3滿足此關係，如上所述，第1庫外熱交換器3A的路徑數Na是2，第2庫外熱交換器3B的路徑數Nb是3以下。The number of paths Na of the first external heat exchanger 3A is an integer of 2 or more, and the number of paths of the second external heat exchanger Nb (Nb: an integer of 2 or more) or less. That is, 2≤Na≤Nb. The external heat exchanger 3 of the refrigeration unit 51 satisfies this relationship. As described above, the number of paths Na of the first external heat exchanger 3A is 2, and the number of paths Nb of the second external heat exchanger 3B is 3 or less.

在第1庫外熱交換器3A中，埠3Aa分歧並連接於路徑P1的一端與路徑P2的一端。埠3Ab分歧並連接於路徑P1的另一端與路徑P2的另一端。亦即，如第7圖所示，路徑P1與路徑P2並聯地連接於埠3Aa與埠3Ab之間。並且，如第4圖所示，路徑P1與路徑P2按照以下方式配置：在送風方向（前後方向）上彼此不重疊，在吸入面上成為實質獨立的區域。In the first external heat exchanger 3A, the port 3Aa is branched and connected to one end of the path P1 and one end of the path P2. The port 3Ab diverges and is connected to the other end of the path P1 and the other end of the path P2. That is, as shown in FIG. 7, the path P1 and the path P2 are connected in parallel between the port 3Aa and the port 3Ab. Furthermore, as shown in FIG. 4, the path P1 and the path P2 are arranged so that they do not overlap with each other in the blowing direction (front-rear direction), and become substantially independent areas on the suction surface.

在第2庫外熱交換器3B中，埠3Ba分歧為三個，並分別連接於路徑P3～P5的一端側。埠3Bb分歧為三個，並分別連接於路徑P3～P5的另一端側。亦即，如第7圖所示，路徑P3～P5並聯地連接於埠3Ba與埠3Bb之間。如第4圖所示，路徑P3～P5按照以下方式配置：在送風方向（前後方向）上彼此大致上沒有相互重疊，而在吸入側的一面（以下，也稱為吸入面）上成為實質獨立的區域。In the second external heat exchanger 3B, the ports 3Ba are branched into three, and they are respectively connected to one end of the paths P3 to P5. The ports 3Bb are divided into three, and they are respectively connected to the other end sides of the paths P3 to P5. That is, as shown in FIG. 7, the paths P3 to P5 are connected in parallel between the port 3Ba and the port 3Bb. As shown in Fig. 4, the paths P3 to P5 are arranged in such a way that they do not substantially overlap each other in the blowing direction (front-rear direction), but become substantially independent on the suction side (hereinafter also referred to as the suction surface) Area.

第1庫外熱交換器3A由於路徑數Na越少，在吸入面上，一個路徑所占的面積越大，因此，第1庫外熱交換器3A容易產生明顯的表面溫度不均。因此，如果增加路徑數Na，在吸入面上，一個路徑所占的面積將會變小，整體表面溫度的不均得以被抑制。亦即，從抑制表面溫度的不均的觀點來看，增加路徑數Na較為理想。另一方面，在設置有二個以上的路徑的情況下，路徑數Na越多，通過路徑的冷媒的流速越低。因此，在設計上，考慮表面溫度的不均的程度與冷媒的流速，以使熱交換功能良好地發揮的方式來設定路徑數Na。例如，可以使第1庫外熱交換器3A的路徑數Na與第2庫外熱交換器3B的路徑數Nb為相同數量(Na＝Nb)，其中，第2庫外熱交換器3B在後述的升溫運轉中作為蒸發器而發揮作用，更佳是，可以使第1庫外熱交換器3A的路徑數Na為第2庫外熱交換器3B的路徑數Nb以下(Na＜Nb)。The smaller the number of paths Na in the first external heat exchanger 3A is, the larger the area occupied by one path on the suction surface is. Therefore, the first external heat exchanger 3A is likely to have significant surface temperature unevenness. Therefore, if the number of paths Na is increased, the area occupied by one path on the suction surface will become smaller, and the unevenness of the overall surface temperature will be suppressed. That is, from the viewpoint of suppressing unevenness in surface temperature, it is preferable to increase the number of paths Na. On the other hand, when two or more paths are provided, the greater the number of paths Na, the lower the flow velocity of the refrigerant passing through the paths. Therefore, in the design, the degree of unevenness in the surface temperature and the flow rate of the refrigerant are considered, and the number of paths Na is set so that the heat exchange function can be performed well. For example, the number of paths Na of the first external heat exchanger 3A and the number of paths Nb of the second external heat exchanger 3B can be the same number (Na=Nb), and the second external heat exchanger 3B will be described later. It functions as an evaporator during the temperature-raising operation, and it is more preferable that the number of paths Na of the first external heat exchanger 3A be equal to or less than the number of paths Nb of the second external heat exchanger 3B (Na<Nb).

考慮埠3Ba與埠3Bb之間的配管長度、此配管的流路面積（配管內徑）、流通於配管內的冷媒的速度等，適當設定第2庫外熱交換器3B的路徑數Nb，以便能使液態冷媒良好地相變化成氣態冷媒。Consider the length of the piping between port 3Ba and port 3Bb, the flow path area of the piping (piping inner diameter), the speed of the refrigerant flowing in the piping, etc., and appropriately set the number of paths Nb of the second external heat exchanger 3B so that It can make a good phase change of liquid refrigerant into gaseous refrigerant.

如第5圖和第6圖所示，多個散熱片3f分別跨設於第1庫外熱交換器3A與第2庫外熱交換器3B上。詳細來說，多個散熱片3f互相靠近且相互平行地相對向並列設置。而且，第1庫外熱交換器3A的冷媒配管線路的配管也就是管3cA（參照第4圖）和第2庫外熱交換器3B的冷媒配管線路的配管也就是管3cB（參照第4圖），以正交貫穿於多個散熱片3f的方式連結。因此，在第1庫外熱交換器3A與第2庫外熱交換器3B之間，經由散熱片3f相互地進行熱傳遞。As shown in Figs. 5 and 6, a plurality of fins 3f are provided across the first external heat exchanger 3A and the second external heat exchanger 3B, respectively. In detail, the plurality of radiating fins 3f are close to each other and arranged in parallel to oppose each other in parallel. Furthermore, the piping of the refrigerant piping line of the first external heat exchanger 3A is pipe 3cA (refer to Fig. 4) and the piping of the refrigerant piping line of the second external heat exchanger 3B is pipe 3cB (refer to Fig. 4) ), which are connected to perpendicularly penetrate through the plurality of radiating fins 3f. Therefore, between the first external heat exchanger 3A and the second external heat exchanger 3B, heat is transferred to each other via the fins 3f.

第1庫外熱交換器3A與第2庫外熱交換器3B，在前後方向上並列設置。詳細來說，第1庫外熱交換器3A是按照以下方式來配置：相對於由風扇FM1的驅動所產生的風的流通方向，而成為上風側。亦即，第1庫外熱交換器3A為上游側熱交換器，第2庫外熱交換器3B為下游側熱交換器。The first external heat exchanger 3A and the second external heat exchanger 3B are arranged side by side in the front-rear direction. Specifically, the first external heat exchanger 3A is arranged so as to be on the windward side with respect to the flow direction of the wind generated by the driving of the fan FM1. That is, the first external heat exchanger 3A is an upstream side heat exchanger, and the second external heat exchanger 3B is a downstream side heat exchanger.

以上詳述的冷凍裝置51可以適用於各種設備和裝置等。例如，載置於冷凍車C。第8圖是表示載置於冷凍車C上的一例的側視圖，其中一部分為切割面。The refrigerating device 51 described in detail above can be applied to various equipment and devices, and the like. For example, it is placed in a refrigerated car C. Fig. 8 is a side view showing an example mounted on the refrigerating vehicle C, and a part of it is a cut surface.

庫內熱交換器5被配置於應在冷凍車C中維持恒溫的庫也就是貨櫃C1（以下，也簡稱為庫C1）的內部空間CV內，與內部空間CV的空氣進行熱交換。在貨櫃C1的外部（例如駕駛座的上方），配置有庫外熱交換器3，與外部空氣進行熱交換。其他構件設置於貨櫃C1的外側，設置位置並無限定。例如，壓縮機1和蓄液器6等被收納於收容體S，並被設置於車體的下方。控制部31和輸入部32被設置於駕駛座附近。尤其是輸入部32，被配置於駕駛員容易操作的地方。壓縮機1的動力源是例如冷凍車C的電池或發動機（均未圖示）。The internal heat exchanger 5 is arranged in the internal space CV of the container C1 (hereinafter also referred to as the "library C1") that should maintain a constant temperature in the refrigerated vehicle C, and exchanges heat with the air in the internal space CV. Outside the container C1 (for example, above the driver's seat), an external heat exchanger 3 is arranged to exchange heat with outside air. The other components are installed on the outside of the container C1, and the installation location is not limited. For example, the compressor 1 and the accumulator 6 are housed in the housing S, and are installed below the vehicle body. The control unit 31 and the input unit 32 are installed near the driver's seat. In particular, the input unit 32 is arranged in a place where the driver can easily operate it. The power source of the compressor 1 is, for example, a battery or an engine of the refrigerated vehicle C (both not shown).

接著，關於冷凍裝置51的運轉動作，基於載置在冷凍車C上的狀態，主要參照第3圖、第7圖、及第9圖～第11圖來進行說明。冷凍裝置51基於由使用者經由輸入部32所作出的指示，選擇性地實行多個模式的運轉，亦即，冷卻運轉、升溫運轉、庫外熱交換器3的除霜運轉、及庫內熱交換器5的除霜運轉，以便使庫C1內成為一定的溫度。Next, the operation operation of the refrigerating device 51 will be described mainly with reference to Figs. 3, 7, and 9 to 11 based on the state of being mounted on the refrigerating vehicle C. The refrigerating device 51 selectively executes a plurality of modes of operation based on instructions given by the user via the input unit 32, that is, cooling operation, warming operation, defrosting operation of the external heat exchanger 3, and internal heat exchange The defrosting operation of the device 5 makes the temperature in the storage C1 constant.

首先，說明冷卻運轉和升溫運轉。第9圖是用以說明冷卻運轉時的冷媒回路的圖。第10圖是用以說明升溫運轉時的冷媒回路的圖。第11圖是用以說明各運轉時的控制部31的控制的表格。在第9圖和第10圖的冷媒回路中，將冷媒流動的配管部位以粗線表示，冷媒的流動方向以粗箭頭表示。First, the cooling operation and the heating operation are explained. Fig. 9 is a diagram for explaining the refrigerant circuit during the cooling operation. Fig. 10 is a diagram for explaining the refrigerant circuit during the heating operation. Fig. 11 is a table for explaining the control of the control unit 31 during each operation. In the refrigerant circuits of Figs. 9 and 10, the piping portion where the refrigerant flows is indicated by thick lines, and the direction of the refrigerant flow is indicated by thick arrows.

（冷卻運轉）如第11圖所示，在冷卻運轉中，控制部31使四通閥2為模式A，電磁閥11為打開狀態，電磁閥13為關閉狀態，風扇FM1和風扇FM2為運轉狀態。在第9圖中，此冷卻運轉中的由風扇FM1和風扇FM2所產生的送風方向，分別以箭頭DR1和箭頭DR2表示。(Cooling operation) As shown in Figure 11, during the cooling operation, the control unit 31 sets the four-way valve 2 to mode A, the solenoid valve 11 is opened, the solenoid valve 13 is closed, and the fan FM1 and fan FM2 are in operation. . In Fig. 9, the blowing directions generated by the fan FM1 and the fan FM2 during this cooling operation are indicated by arrows DR1 and DR2, respectively.

如第9圖所示，根據控制部31的控制，由壓縮機1的吐出口吐出的高壓氣態冷媒，從成為模式A的四通閥2的埠2a，經過埠2b而流入配管線路L2。流入配管線路L2中的氣態冷媒，從埠3Ba供給至庫外熱交換器3中的第2庫外熱交換器3B中，流經路徑P3～P5中的任一路徑，然後從埠3Bb以氣液混合冷媒的形式流出。從埠3Bb流出的氣液混合冷媒，經過止回閥9，從埠3Ab供給至第1庫外熱交換器3A，流經路徑P1和路徑P2中的任一路徑，然後從埠3Aa流出。As shown in FIG. 9, under the control of the control unit 31, the high-pressure gaseous refrigerant discharged from the discharge port of the compressor 1 flows from the port 2a of the four-way valve 2 of the mode A through the port 2b into the piping line L2. The gaseous refrigerant flowing into the piping line L2 is supplied from the port 3Ba to the second external heat exchanger 3B in the external heat exchanger 3, flows through any one of the paths P3 to P5, and then flows from the port 3Bb to the second external heat exchanger 3B. It flows out in the form of liquid mixed refrigerant. The gas-liquid mixed refrigerant flowing out from the port 3Bb passes through the check valve 9 and is supplied from the port 3Ab to the first external heat exchanger 3A, flows through any one of the path P1 and the path P2, and then flows out from the port 3Aa.

在庫外熱交換器3中，風扇FM1根據控制部31的控制而處於運轉狀態，外部空氣向第9圖的箭頭DR1方向流動。此狀態下，在庫外熱交換器3中，第2庫外熱交換器3B與第1庫外熱交換器3A作為一體的冷凝器而發揮功能。亦即，氣態冷媒對外部空氣散熱而冷凝，以高壓液態冷媒的形式從埠3Aa流入配管線路L5。詳細來說，冷媒在第2庫外熱交換器3B的入口也就是埠3Ba處，全部為氣相。氣相的冷媒(氣態冷媒)隨著於第2庫外熱交換器3B內流動，而與外部空氣進行熱交換，部分氣態冷媒冷凝（液化），液態冷媒相對於氣態冷媒的比率增加。這樣一來，在第2庫外熱交換器3B的出口也就是埠3Bb處，冷媒成為液態冷媒與氣態冷媒混合在一起的氣液混合冷媒。此處，液態冷媒的比率隨著運轉條件而不同。In the external heat exchanger 3, the fan FM1 is in an operating state under the control of the control unit 31, and the outside air flows in the direction of the arrow DR1 in Fig. 9. In this state, in the external heat exchanger 3, the second external heat exchanger 3B and the first external heat exchanger 3A function as an integrated condenser. That is, the gaseous refrigerant radiates heat to the outside air and condenses, and flows into the piping line L5 from the port 3Aa in the form of a high-pressure liquid refrigerant. Specifically, the refrigerant is in the gas phase at the inlet of the second external heat exchanger 3B, which is the port 3Ba. As the refrigerant in the gas phase (gas refrigerant) flows in the second external heat exchanger 3B, it exchanges heat with the outside air, part of the gas refrigerant is condensed (liquefied), and the ratio of the liquid refrigerant to the gas refrigerant increases. In this way, at the outlet of the second external heat exchanger 3B, which is the port 3Bb, the refrigerant becomes a gas-liquid mixed refrigerant in which a liquid refrigerant and a gaseous refrigerant are mixed. Here, the ratio of the liquid refrigerant varies depending on the operating conditions.

接著，從埠3Bb流出的氣液混合冷媒，從埠3Ab流入第1庫外熱交換器3A。利用第1庫外熱交換器3A，繼續進行冷媒與外部空氣的熱交換，在出口也就是埠3Aa中，冷媒在高壓下大致全部成為液相(液態)。Next, the gas-liquid mixed refrigerant flowing out of the port 3Bb flows into the first external heat exchanger 3A from the port 3Ab. With the first external heat exchanger 3A, the heat exchange between the refrigerant and the outside air is continued, and in the outlet port 3Aa, the refrigerant becomes almost all in the liquid phase (liquid state) under high pressure.

由於冷媒在庫外熱交換器3中從氣相向液相發生相變化，而使冷媒的體積減少。在庫外熱交換器3中，因體積減少而導致液相比率變高的冷媒所流通的第1庫外熱交換器3A的路徑數Na，少於氣相比率較高的冷媒所流通的第2庫外熱交換器3B的路徑數Nb。這樣一來，流通於第1庫外熱交換器3A內的冷媒，與以液態冷媒的形式流通於第2庫外熱交換器3B時相比，質量流速變大，冷媒的過冷度也變大。Since the refrigerant undergoes a phase change from the gas phase to the liquid phase in the external heat exchanger 3, the volume of the refrigerant is reduced. In the external heat exchanger 3, the number of paths Na of the first external heat exchanger 3A through which the refrigerant with a higher liquid phase ratio circulates due to the decrease in volume is less than that of the second external heat exchanger 3A through which the refrigerant with a higher gas phase ratio circulates. The number of paths Nb of the external heat exchanger 3B. As a result, the refrigerant circulating in the first external heat exchanger 3A has a higher mass flow rate and a higher degree of subcooling of the refrigerant than when the refrigerant circulates in the second external heat exchanger 3B in the form of liquid refrigerant. Big.

流入配管線路L5中的高壓液態冷媒，通過止回閥10，進入受液器4。在受液器4中，滯留與運轉環境相對應的剩餘量的液態冷媒。例如，當庫C1內的熱負荷較小時，循環的冷媒的量可以較少，在受液器4內積存較多的液態冷媒。另一方面，當庫C1內的熱負荷較大時，由於循環的冷媒的量需要較多，因此積存於受液器4內的液態冷媒的量變少。受液器4成為以下構造：當有液態冷媒積存時，使液態冷媒流出。The high-pressure liquid refrigerant flowing into the piping line L5 passes through the check valve 10 and enters the receiver 4. In the receiver 4, the remaining amount of liquid refrigerant corresponding to the operating environment is retained. For example, when the thermal load in the storage C1 is small, the amount of circulating refrigerant may be small, and a large amount of liquid refrigerant may be accumulated in the receiver 4. On the other hand, when the thermal load in the storage C1 is large, the amount of circulating refrigerant needs to be large, and therefore the amount of liquid refrigerant accumulated in the receiver 4 becomes small. The receiver 4 has a structure that allows the liquid refrigerant to flow out when the liquid refrigerant is accumulated.

根據控制部31的控制使電磁閥13關閉，並使電磁閥11打開，因此，從受液器4流出的液態冷媒流入配管線路L6。亦即，流入配管線路L6中的液態冷媒，經過電磁閥11進入膨脹閥12。在膨脹閥12中，液態冷媒膨脹。這樣一來，液態冷媒由於壓力和溫度降低，氣化被促進，而成為氣相與液相混合的氣液混合冷媒。從膨脹閥12流出的氣液混合冷媒，流入庫內熱交換器5。The solenoid valve 13 is closed and the solenoid valve 11 is opened under the control of the control unit 31. Therefore, the liquid refrigerant flowing out of the receiver 4 flows into the piping line L6. That is, the liquid refrigerant flowing into the piping line L6 passes through the solenoid valve 11 and enters the expansion valve 12. In the expansion valve 12, the liquid refrigerant expands. In this way, the liquid refrigerant is reduced in pressure and temperature, and gasification is promoted, and it becomes a gas-liquid mixed refrigerant in which the gas phase and the liquid phase are mixed. The gas-liquid mixed refrigerant flowing out of the expansion valve 12 flows into the internal heat exchanger 5.

在庫內熱交換器5中，風扇FM2根據控制部31的控制而處於運轉狀態，使庫C1內的空氣向第9圖的箭頭DR2的方向流動。在此狀態下，氣液混合冷媒與庫C1內的空氣進行熱交換，從庫C1內的空氣獲取熱量，完全地氣化，而成為氣態冷媒。亦即，庫內熱交換器5作為蒸發器而發揮功能，於是庫C1內被冷卻。In the internal heat exchanger 5, the fan FM2 is in an operating state under the control of the control unit 31, and causes the air in the compartment C1 to flow in the direction of the arrow DR2 in FIG. 9. In this state, the gas-liquid mixed refrigerant exchanges heat with the air in the storage C1, obtains heat from the air in the storage C1, is completely vaporized, and becomes a gaseous refrigerant. That is, the internal heat exchanger 5 functions as an evaporator, so the inside of the library C1 is cooled.

從庫內熱交換器5流出的氣態冷媒，流入配管線路L8。在配管線路L8中，由於氣態冷媒在分歧部D3的壓力低於配管線路L5中的分歧部D1的壓力，因此，不會流入配管線路L9，而是經過止回閥14到達四通閥2。由於四通閥2根據控制部31的控制而成為模式A，因此，氣態冷媒從埠2d流經埠2c，進一步流經蓄液器6並返回至壓縮機1的吸入口。The gaseous refrigerant flowing out of the internal heat exchanger 5 flows into the piping line L8. In the piping line L8, since the pressure of the gaseous refrigerant at the branch D3 is lower than the pressure at the branch D1 of the piping line L5, it does not flow into the piping line L9, but passes through the check valve 14 to the four-way valve 2. Since the four-way valve 2 becomes the mode A under the control of the control unit 31, the gaseous refrigerant flows from the port 2d through the port 2c, and further flows through the accumulator 6 and returns to the suction port of the compressor 1.

（升溫運轉）如第11圖所示，在升溫運轉中，控制部31使四通閥2為模式B，電磁閥11為關閉狀態，電磁閥13為打開狀態，風扇FM1和風扇FM2為運轉狀態。此升溫運轉中的風扇FM1和風扇FM2的送風方向，與冷卻運轉相同為一定的方向，在第10圖中分別以箭頭DR3和箭頭DR4表示。(Temperature heating operation) As shown in Figure 11, during the heating operation, the control unit 31 sets the four-way valve 2 to mode B, the solenoid valve 11 is closed, the solenoid valve 13 is opened, and the fan FM1 and fan FM2 are in operation. . The blowing direction of the fan FM1 and the fan FM2 during the heating operation is the same as the cooling operation, and is a constant direction, and is indicated by an arrow DR3 and an arrow DR4 in FIG. 10, respectively.

如第10圖所示，根據控制部31的控制，由壓縮機1的吐出口吐出的高壓氣態冷媒，從成為模式B的四通閥2的埠2a，經過埠2d而流入配管線路L8。接著，氣態冷媒從分歧部D4流入配管線路L10，並進入受液器4。As shown in FIG. 10, under the control of the control unit 31, the high-pressure gaseous refrigerant discharged from the discharge port of the compressor 1 flows into the piping line L8 from the port 2a of the four-way valve 2 in the mode B through the port 2d. Next, the gaseous refrigerant flows into the piping line L10 from the branch D4 and enters the receiver 4.

在受液器4中，氣態冷媒將之前的冷卻運轉中所積存的液態冷媒擠出，很快充滿受液器4內。因此，氣態冷媒隨著積存量的液態冷媒之後，從受液器4流出。根據控制部31的控制使電磁閥13成為打開狀態，電磁閥11成為關閉狀態，因此，從受液器4流出的氣態冷媒流入配管線路L7，接著流入庫內熱交換器5。In the receiver 4, the gaseous refrigerant squeezes out the liquid refrigerant accumulated in the previous cooling operation, and fills the receiver 4 quickly. Therefore, the gaseous refrigerant flows out of the receiver 4 following the accumulated amount of liquid refrigerant. According to the control of the control unit 31, the solenoid valve 13 is opened and the solenoid valve 11 is closed. Therefore, the gaseous refrigerant flowing out of the receiver 4 flows into the piping line L7, and then flows into the internal heat exchanger 5.

在庫內熱交換器5中，如上所述，風扇FM2根據控制部31的控制而處於運轉狀態，庫C1內的空氣向第10圖的箭頭DR4方向流動。在此狀態下，氣態冷媒與庫C1內的空氣進行熱交換，向庫C1內的空氣放出熱量而冷凝，大致成為高壓液態冷媒。因此，庫C1內升溫。In the internal heat exchanger 5, as described above, the fan FM2 is in an operating state under the control of the control unit 31, and the air in the compartment C1 flows in the direction of the arrow DR4 in FIG. 10. In this state, the gaseous refrigerant exchanges heat with the air in the storage C1, releases heat to the air in the storage C1, condenses, and substantially becomes a high-pressure liquid refrigerant. Therefore, the temperature in the library C1 is increased.

在從庫內熱交換器5流出的冷媒中，含有液態冷媒，並且含有與庫C1內的熱負荷等運轉環境相對應的量的氣態冷媒。由於在分歧部D3處，壓力低於分歧部D4，因此，此含有該液態冷媒與氣態冷媒的氣液混合冷媒流入配管線路L9。然後，流經止回閥15，從埠3Aa流入庫外熱交換器3的第1庫外熱交換器3A。The refrigerant flowing out of the internal heat exchanger 5 contains liquid refrigerant and also contains gaseous refrigerant in an amount corresponding to the operating environment such as the heat load in the storage C1. Since the pressure at the branch D3 is lower than that at the branch D4, the gas-liquid mixed refrigerant containing the liquid refrigerant and the gaseous refrigerant flows into the piping line L9. Then, it flows through the check valve 15 and flows into the first external heat exchanger 3A of the external heat exchanger 3 from the port 3Aa.

在庫外熱交換器3中，風扇FM1根據控制部31的控制而處於運轉狀態，外部空氣向第10圖的箭頭DR3方向流動。因此，第1庫外熱交換器3A相對於第2庫外熱交換器3B，位於外部空氣流通的上游側。此狀態下，在第1庫外熱交換器3A內，液態冷媒被冷卻，溫度下降。亦即，第1庫外熱交換器3A對於液態冷媒，作為過冷卻熱交換器而發揮功能。與液態冷媒一起流入第1庫外熱交換器3A中的氣態冷媒，根據此冷卻，也大致全部成為液態冷媒。In the external heat exchanger 3, the fan FM1 is in an operating state under the control of the control unit 31, and the outside air flows in the direction of the arrow DR3 in Fig. 10. Therefore, the first external heat exchanger 3A is located on the upstream side of the flow of outside air with respect to the second external heat exchanger 3B. In this state, the liquid refrigerant is cooled in the first external heat exchanger 3A, and the temperature drops. That is, the first external heat exchanger 3A functions as a supercooling heat exchanger for the liquid refrigerant. The gaseous refrigerant flowing into the first external heat exchanger 3A together with the liquid refrigerant is cooled by this, and almost all becomes the liquid refrigerant.

過冷卻後的液態冷媒，從第1庫外熱交換器3A的埠3Ab流出，並流入配管線路L3。在配管線路L3中，液態冷媒經過止回閥8而進入膨脹閥7。在膨脹閥7中，液態冷媒膨脹。這樣一來，液態冷媒由於壓力和溫度降低，氣化被促進，而成為混合有氣相與液相的氣液混合冷媒。從膨脹閥7流出的氣液混合冷媒，從埠3Bb流入第2庫外熱交換器3B。在第2庫外熱交換器3B中，從埠3Bb流入的氣液混合冷媒，利用與外部空氣的熱交換，從外部空氣獲取熱量而蒸發，並成為氣態冷媒，從埠3Ba流入配管線路L2。亦即，第2庫外熱交換器3B作為蒸發器而發揮功能。流入配管線路L2中的氣態冷媒，從成為模式B的四通閥2的埠2b經過埠2c，流經蓄液器6並返回至壓縮機1的吸入口。The supercooled liquid refrigerant flows out of the port 3Ab of the first external heat exchanger 3A, and flows into the piping line L3. In the piping line L3, the liquid refrigerant passes through the check valve 8 and enters the expansion valve 7. In the expansion valve 7, the liquid refrigerant expands. In this way, the pressure and temperature of the liquid refrigerant are reduced, and gasification is promoted to become a gas-liquid mixed refrigerant in which a gas phase and a liquid phase are mixed. The gas-liquid mixed refrigerant flowing out of the expansion valve 7 flows into the second external heat exchanger 3B from the port 3Bb. In the second external heat exchanger 3B, the gas-liquid mixed refrigerant flowing in from the port 3Bb obtains heat from the outside air to evaporate by heat exchange with the outside air, becomes a gaseous refrigerant, and flows into the piping line L2 from the port 3Ba. That is, the second external heat exchanger 3B functions as an evaporator. The gaseous refrigerant flowing into the piping line L2 passes through the port 2b of the four-way valve 2 in the mode B, passes through the port 2c, flows through the accumulator 6 and returns to the suction port of the compressor 1.

在此升溫運轉中，冷凍裝置51獲得以下效果。In this heating operation, the refrigeration device 51 obtains the following effects.

使用四通閥進行冷卻運轉與升溫運轉的切換，在升溫運轉中，不僅利用壓縮機動作所獲得的熱量進行升溫，還利用由庫外熱交換器從外部空氣所獲得的熱量進行升溫。因此，獲得較高的升溫能力。The four-way valve is used to switch between the cooling operation and the heating operation. In the heating operation, not only the heat obtained by the compressor operation is used to raise the temperature, but also the heat obtained from the outside air by the external heat exchanger is used to raise the temperature. Therefore, a higher temperature raising ability is obtained.

冷卻運轉與升溫運轉的切換，僅利用四通閥與電磁閥的切換來實行，而無需根據壓力感測器等的測定結果來進行控制。因此，運轉動作的控制簡單。The switching between the cooling operation and the heating operation is performed only by switching between the four-way valve and the solenoid valve, and there is no need to perform control based on the measurement result of the pressure sensor or the like. Therefore, the control of the running action is simple.

在第2庫外熱交換器3B中，氣液混合冷媒進行從外部空氣獲取熱量的熱交換，成為低壓氣態冷媒。在庫外熱交換器3中，多個散熱片3f以橫跨第1庫外熱交換器3A與第2庫外熱交換器3B的方式設置。因此，在第1庫外熱交換器3A中，液態冷媒所放出的部分熱量傳遞至散熱片3f並移動至第2庫外熱交換器，作為在第2庫外熱交換器中的相變化的蒸發熱而被利用。這樣一來，由於第2庫外熱交換器中的液態冷媒的蒸發得以被促進，因此，可以防止液態冷媒被吸入至壓縮機，也就是所謂的液擊(回液)現象的產生。In the second external heat exchanger 3B, the gas-liquid mixed refrigerant performs heat exchange to obtain heat from the outside air, and becomes a low-pressure gas refrigerant. In the external heat exchanger 3, a plurality of fins 3f are provided so as to straddle the first external heat exchanger 3A and the second external heat exchanger 3B. Therefore, in the first external heat exchanger 3A, part of the heat released by the liquid refrigerant is transferred to the fins 3f and moved to the second external heat exchanger as a phase change in the second external heat exchanger The heat of evaporation is used. In this way, since the evaporation of the liquid refrigerant in the second external heat exchanger is promoted, it is possible to prevent the liquid refrigerant from being sucked into the compressor, which is the so-called liquid hammer (liquid return) phenomenon.

並且，即便當運轉環境為例如在寒冷地區中行車，因降雪而使散熱片3f上積雪時，附著於散熱片3f上的雪，也會因散熱片3f受到第1庫外熱交換器隨著升溫運轉而進行的熱交換所放出的熱量而變得溫熱，從而融化。並且，每一個散熱片3f在第2庫外熱交換器3B側的部分，由於以下原因而變得溫熱：因利用在第1庫外熱交換器3A的熱交換而被升溫的外部空氣，向下游側流通；及，利用在第1庫外熱交換器3A中的熱交換賦予散熱片3f的熱量，向散熱片3f的下游側傳遞。這樣一來，由於全部散熱片3f均高效率地變暖，因此，極為有效地防止散熱片3f上的積雪或結霜。因此，冷凍裝置51的除霜動作的實行間隔變長，動作效率提高。Moreover, even when the operating environment is, for example, driving in a cold area and snow accumulates on the fins 3f due to snowfall, the snow adhering to the fins 3f will be affected by the first external heat exchanger due to the fins 3f. The heat released by the heat exchange during the heating operation becomes warm and melts. In addition, the portion of each fin 3f on the side of the second external heat exchanger 3B becomes warm due to the following reasons: the outside air heated by the heat exchange in the first external heat exchanger 3A, Circulate to the downstream side; and, the heat imparted to the fin 3f by heat exchange in the first external heat exchanger 3A is transferred to the downstream side of the fin 3f. In this way, since all the heat sinks 3f are warmed efficiently, it is extremely effective to prevent snow or frost on the heat sinks 3f. Therefore, the execution interval of the defrosting operation of the refrigerating device 51 becomes longer, and the operation efficiency is improved.

在此升溫運轉中，在受液器4中，並無液態冷媒滯留。另一方面，對應於包括庫C1內的熱負荷在內的運轉環境，冷媒回路所需要的冷媒循環量發生變化。因此，在冷凍裝置51的第1庫外熱交換器3A中，存在液態冷媒及與運轉環境相對應的量的氣態冷媒。換句話說，第1庫外熱交換器3A，在升溫運轉中代替受液器4來調整並確保剩餘的液態冷媒，以便使冷媒回路內循環有最適合運轉環境的冷媒量。這樣一來，可以將冷媒回路的高壓側的壓力維持在較高的值。因此，庫內熱交換器5中的冷媒冷凝溫度變高，升溫能力提高。During this heating operation, no liquid refrigerant remains in the receiver 4. On the other hand, in accordance with the operating environment including the heat load in the storage C1, the amount of refrigerant circulation required by the refrigerant circuit changes. Therefore, in the first external heat exchanger 3A of the refrigerating device 51, there are liquid refrigerant and gaseous refrigerant in an amount corresponding to the operating environment. In other words, the first external heat exchanger 3A replaces the receiver 4 during the warming operation to adjust and secure the remaining liquid refrigerant so that the refrigerant circuit circulates the refrigerant amount that is most suitable for the operating environment. In this way, the pressure on the high-pressure side of the refrigerant circuit can be maintained at a high value. Therefore, the condensation temperature of the refrigerant in the internal heat exchanger 5 becomes higher, and the temperature raising ability improves.

冷凍裝置51，根據使用流通方向限制部RK等，使在冷卻運轉與升溫運轉中，流通於庫內熱交換器5中的冷媒的方向相同。並且，使在冷卻運轉與升溫運轉中，利用風扇FM2的運轉所產生的氣流方向也相同。並且，如第9圖和第10圖所示，庫內熱交換器5中的冷媒的流通方向可以為：以與送風方向（箭頭DR2、DR4）相對向的方式，從下游側朝向上游側（從下游側流入，從上游側流出）。由於以上等原因，在冷卻運轉時的熱交換效率與在升溫運轉中的熱交換效率之間，不會產生明顯的差異。這樣一來，熱交換效率進一步提高。The refrigerating device 51 uses the flow direction restricting portion RK or the like to make the direction of the refrigerant flowing in the indoor heat exchanger 5 the same during the cooling operation and the temperature raising operation. In addition, the direction of the airflow generated by the operation of the fan FM2 is also the same in the cooling operation and the heating operation. Also, as shown in Figures 9 and 10, the flow direction of the refrigerant in the internal heat exchanger 5 may be such that it faces the blowing direction (arrows DR2 and DR4) from the downstream side to the upstream side (from the Inflow from the downstream side and outflow from the upstream side). Due to the above and other reasons, there is no significant difference between the heat exchange efficiency during the cooling operation and the heat exchange efficiency during the heating operation. In this way, the heat exchange efficiency is further improved.

在冷卻運轉與升溫運轉中，被封入冷媒回路中的冷媒量相同。亦即，由於在升溫運轉中，受液器4內並不貯存液態冷媒，因此，冷卻運轉時滯留於受液器4中的液態冷媒，在升溫運轉時，在第1庫外熱交換器3A內調整並確保該液態冷媒的量。詳細來說，第1庫外熱交換器3A內的液態冷媒的確保量，是利用使液態冷媒的氣化量（氣態冷媒的量）變化來調整。關於在此第1庫外熱交換器3A中的液態冷媒量的調整功能，根據實驗，獲得以下結論：較理想為，將第1庫外熱交換器3A的液態冷媒的容量Qa，設定為不超過受液器4的液態冷媒的容量Qb的值（亦即，Qa≤Qb）。此容量Qa的調整設定，利用例如增減第1庫外熱交換器3A中的管3c的列數來進行。亦即，M列N段的第1庫外熱交換器3A，是將其中的一列作成特定容量的定型構造，並將此定型構造沿著風扇FM1的送風方向並列設置M個而成。此時，較理想為，使M的值為在第1庫外熱交換器3A的容量不超過受液器4的容量的範圍內的最大值。In the cooling operation and the heating operation, the amount of refrigerant enclosed in the refrigerant circuit is the same. That is, since the liquid refrigerant is not stored in the receiver 4 during the heating operation, the liquid refrigerant remaining in the receiver 4 during the cooling operation is transferred to the first external heat exchanger 3A during the heating operation. Internally adjust and ensure the amount of liquid refrigerant. Specifically, the secured amount of liquid refrigerant in the first external heat exchanger 3A is adjusted by changing the vaporization amount of the liquid refrigerant (amount of gaseous refrigerant). Regarding the adjustment function of the amount of liquid refrigerant in the first external heat exchanger 3A, based on experiments, the following conclusions have been obtained: It is more desirable to set the liquid refrigerant capacity Qa of the first external heat exchanger 3A to not A value exceeding the capacity Qb of the liquid refrigerant of the receiver 4 (that is, Qa≦Qb). The adjustment setting of this capacity Qa is performed by, for example, increasing or decreasing the number of rows of tubes 3c in the first external heat exchanger 3A. That is, the first external heat exchanger 3A of the M row and the N stage is formed by setting one of the rows into a fixed structure with a specific capacity, and setting M of this fixed structure in parallel along the blowing direction of the fan FM1. At this time, it is preferable to set the value of M to the maximum value in a range in which the capacity of the first external heat exchanger 3A does not exceed the capacity of the liquid receiver 4.

接著，對除霜運轉進行說明。Next, the defrosting operation will be described.

（庫內熱交換器5的除霜運轉）如果長時間進行冷卻運轉，就可能會使庫C1內的空氣中所含有的水分結冰成霜，並附著於庫內熱交換器5的散熱片上。由於散熱片上的結霜會阻礙熱交換，因此，實行庫內熱交換器5的除霜運轉以便除霜。如第11圖所示，此除霜運轉，只有在使風扇FM1和風扇FM2停止方面，不同於升溫運轉。(Defrosting operation of internal heat exchanger 5) If the cooling operation is performed for a long time, the moisture contained in the air in the storage C1 may freeze into frost and adhere to the fins of the internal heat exchanger 5. Since frost on the radiating fins hinders heat exchange, the defrosting operation of the internal heat exchanger 5 is performed to defrost. As shown in Fig. 11, this defrosting operation differs from the heating operation only in stopping the fan FM1 and the fan FM2.

（庫外熱交換器3的除霜運轉）如果長時間進行升溫運轉，就可能會使外部空氣中所含有的水分結冰成霜，並附著於庫外熱交換器3的散熱片3f上。如上所述，在冷凍裝置51中，庫外熱交換器3的散熱片3f上的積雪或結霜極其不易產生。但是，當使冷凍車C在降雪時行車的時候，如果降雪量明顯較多，庫外熱交換器3的上風側（第1庫外熱交換器3A側）的鄰接的散熱片3f之間也可能會堵塞。此時，由於熱交換受到阻礙，因此，實行庫外熱交換器3的除霜運轉，對散熱片3f實行融雪和除霜。如第11圖所示，此除霜運轉，只有在使風扇FM1和風扇FM2停止方面，不同於冷卻運轉。(Defrosting operation of the external heat exchanger 3) If the temperature increase operation is performed for a long time, the moisture contained in the outside air may freeze and become frost, and it may adhere to the fins 3f of the external heat exchanger 3. As described above, in the refrigerating device 51, the accumulation of snow or frost on the fins 3f of the external heat exchanger 3 is extremely difficult to generate. However, when the refrigerated vehicle C is driven during snowfall, if the amount of snowfall is significantly greater, the space between the adjacent fins 3f on the windward side of the external heat exchanger 3 (the side of the first external heat exchanger 3A) It may also be blocked. At this time, since the heat exchange is hindered, the defrosting operation of the external heat exchanger 3 is performed, and snow melting and defrosting are performed on the fins 3f. As shown in Figure 11, this defrosting operation differs from the cooling operation only in stopping the fan FM1 and the fan FM2.

庫外熱交換器3的具體參數，例如設定如下：第1庫外熱交換器3A的前後方向的厚度Ea（參照第5圖）：19.05 mm 第2庫外熱交換器3B的前後方向的厚度Eb（參照第5圖）：57.15 mm 前後方向的總厚度(Ea+Eb)：76.20 mm 上下方向的高度Ec（參照第5圖）：355.6 mm 左右方向的有效寬度（通風部分的寬度）Ed（參照第5圖）：1050 mm 冷媒配管直徑（外徑）：φ9.53 mm 冷媒配管的間距Ee（參照第4圖）：25.4 mmThe specific parameters of the external heat exchanger 3 are, for example, set as follows: The thickness Ea of the first external heat exchanger 3A in the front-rear direction (refer to Fig. 5): 19.05 mm The thickness of the second external heat exchanger 3B in the front-rear direction Eb (refer to Figure 5): 57.15 mm Total thickness in the front and rear direction (Ea+Eb): 76.20 mm Height in the vertical direction Ec (refer to Figure 5): 355.6 mm Effective width in the left and right direction (width of the ventilation part) Ed ( Refer to Figure 5): 1050 mm Diameter of refrigerant piping (outer diameter): φ9.53 mm Pitch Ee of refrigerant piping (refer to Figure 4): 25.4 mm

[冷卻運轉時（庫外熱交換器3作為冷凝器而發揮功能）] 散熱量：4.8 kW 冷媒配管內的冷媒流量：約1.14 kg/min 第1庫外熱交換器3A的配管內冷媒的流速：0.165 公尺/秒(m/s)（液相狀態）第2庫外熱交換器3B的配管內冷媒的流速：1.05 m/s（氣相狀態）、0.11 m/s（液相狀態）[During cooling operation (external heat exchanger 3 functions as a condenser)] Heat dissipation capacity: 4.8 kW Refrigerant flow rate in the refrigerant pipe: Approximately 1.14 kg/min Flow velocity of the refrigerant in the pipe of the first external heat exchanger 3A : 0.165 m/s (m/s) (liquid state) The flow velocity of the refrigerant in the pipes of the second external heat exchanger 3B: 1.05 m/s (gas state), 0.11 m/s (liquid state)

[升溫運轉時（庫外熱交換器3至少作為蒸發器而發揮功能）] 吸熱量：2.5 kW 冷媒配管內的冷媒流量：約2.10 kg/min 第1庫外熱交換器3A的配管內冷媒的流速：0.260 m/s（液相狀態）第2庫外熱交換器3B的配管內冷媒的流速：6.45 m/s（氣相狀態）、0.173m/s（液相狀態）第1庫外熱交換器3A的入口處的冷媒溫度：20℃ 第1庫外熱交換器3A的出口處的冷媒溫度：5℃[During heating operation (external heat exchanger 3 functions at least as an evaporator)] Heat absorption: 2.5 kW Refrigerant flow rate in the refrigerant pipe: Approximately 2.10 kg/min of the refrigerant in the pipe of the first external heat exchanger 3A Flow velocity: 0.260 m/s (liquid phase state) Flow velocity of the refrigerant in the piping of the second external heat exchanger 3B: 6.45 m/s (gas phase state), 0.173 m/s (liquid phase state) No. 1 external heat The temperature of the refrigerant at the inlet of the exchanger 3A: 20°C The temperature of the refrigerant at the outlet of the first external heat exchanger 3A: 5°C

庫外熱交換器3的參數設定為其他規格，以獲得尤其是在冷卻運轉中的散熱量（上述例中為4.8 kW)。作為設定步驟例，首先，由於第2庫外熱交換器3B在冷卻運轉時作為冷凝器而發揮功能，並且在升溫運轉時作為蒸發器而發揮功能，因此，考慮冷卻運轉時的參數與升溫運轉時的參數，設定為3列（作為冷凝器為4列）14段3路徑（步驟「A」）。接著，採用例如更佳路徑數條件也就是Na＜Nb，使第1庫外熱交換器3A的路徑為2。進一步，使列數M為在第1庫外熱交換器3A的容量不超過受液器4的容量的範圍內的最大值而算出的1。在此種步驟中，規格設定為例如1列14段2路徑（步驟「B」）。The parameters of the external heat exchanger 3 are set to other specifications to obtain heat dissipation especially during cooling operation (4.8 kW in the above example). As an example of the setting procedure, firstly, since the second external heat exchanger 3B functions as a condenser during the cooling operation and functions as an evaporator during the temperature-rising operation, consider the parameters and the temperature-rising operation during the cooling operation. The parameters at the time are set to 3 rows (4 rows as a condenser), 14 steps, 3 paths (step "A"). Next, for example, the better path number condition, that is, Na<Nb, is used to set the path of the first external heat exchanger 3A to 2. Furthermore, the number of columns M is calculated to be 1, which is the maximum value in the range in which the capacity of the first external heat exchanger 3A does not exceed the capacity of the liquid receiver 4. In this step, the specification is set to, for example, 1 row, 14 segments and 2 paths (step "B").

如上所述，在第1庫外熱交換器3A的散熱片3f上有積雪時，庫外熱交換器3可以利用升溫運轉使此雪融化。第1庫外熱交換器3A只要放出使積雪融化的熱量即可，多餘的熱量只是耗費於對已融化的水進行升溫而徒勞無功。並且，由於積雪遍及第1庫外熱交換器3A的整個吸入面，因此，較佳為，並非局部融化，而是使融化區域盡可能分散於整個吸入面。如參數例所示，第1庫外熱交換器3A中的入口與出口的冷媒溫度的差值，為例如15℃(deg)。例如，如果使路徑數Na為1，入口為上方側，出口為下方側，就會僅使上方側成為最高溫，下方側成為最低溫，在上下方向產生緩和的溫度梯度。因此，當產生融化區域與非融化區域時，是在上下方向分成兩部分。As described above, when snow accumulates on the fins 3f of the first external heat exchanger 3A, the external heat exchanger 3 can melt the snow by the heating operation. The first external heat exchanger 3A only needs to release the heat that melts the snow, and the excess heat is only used to raise the temperature of the melted water, which is in vain. In addition, since the snow accumulates over the entire suction surface of the first external heat exchanger 3A, it is preferable to disperse the melting area over the entire suction surface as much as possible instead of locally melting. As shown in the parameter example, the difference between the inlet and outlet refrigerant temperatures in the first external heat exchanger 3A is, for example, 15°C (deg). For example, if the number of paths Na is 1, the inlet is on the upper side, and the outlet is on the lower side, only the upper side becomes the highest temperature and the lower side becomes the lowest temperature, and a gentle temperature gradient is generated in the vertical direction. Therefore, when the melting area and the non-melting area are generated, it is divided into two parts in the up and down direction.

對此，使路徑數Na為例如像實施例一樣為2，在吸入面上將各路徑實質上所占的區域分離成上方側與下方側而設置。進一步，可以在上方側設置一路徑的入口，在下方側設置另一路徑的出口，在上下方向的中央部位配置上方側的路徑的出口與下方側的路徑的入口。此時，由於吸入面的上下方向的溫度梯度從上方側朝向下方側，呈「高-低-高-低」，因此當存在融化區域與非融化區域時，交替地出現2次融化與非融化也就是「融化-非融化-融化-非融化」。因此，融化區域被分散而較佳。由於路徑數Na越大，此分散越細膩地擴展，因此較佳。並且，路徑數Na越大，高溫範圍也越不集中而分散。因此，能夠抑制對融化的水進行升溫的多餘的熱量的放出，因而較佳。這樣一來，較佳是使路徑數Na為2以上。In this regard, the number of paths Na is, for example, 2 as in the embodiment, and the area substantially occupied by each path is divided into an upper side and a lower side on the suction surface. Furthermore, an entrance of one path may be provided on the upper side, an exit of another path may be provided on the lower side, and the exit of the upper path and the entrance of the lower path may be arranged at the center of the vertical direction. At this time, since the temperature gradient in the vertical direction of the suction surface is "high-low-high-low" from the upper side to the lower side, when there is a melting area and a non-melting area, two melting and non-melting occur alternately. That is, "melting-non-melting-melting-non-melting". Therefore, the melting area is dispersed and better. Since the larger the number of paths Na, the more finely this dispersion spreads, which is better. In addition, the greater the number of paths Na, the less concentrated and dispersed the high temperature range. Therefore, it is possible to suppress the release of excess heat that raises the temperature of the melted water, which is preferable. In this way, the number of paths Na is preferably 2 or more.

實施例的庫外熱交換器3和冷凍裝置51並非限定於上述構成，在不脫離本發明的要旨的範圍內，也可以作成變化例。The external heat exchanger 3 and the refrigerating device 51 of the embodiment are not limited to the above-mentioned configuration, and they may be modified as long as they do not deviate from the gist of the present invention.

（變化例1）變化例1是在冷凍裝置51的冷媒回路中，在庫內熱交換器5的上游側的配管線路L6與下游側的配管線路L8之間，設置進行熱交換的氣液熱交換器17（冷凍裝置51A）（參照第12圖）的例子。第12圖是主要表示在冷凍裝置51A的冷媒回路中的與冷凍裝置51的冷媒回路（參照第1圖）不同的部分的局部回路圖。氣液熱交換器17，相對於配管線路L6，連接於電磁閥11與膨脹閥12之間。並且，相對於配管線路L8，連接於庫內熱交換器5與分歧部D3之間。(Modification 1) Modification 1 is that in the refrigerant circuit of the refrigeration unit 51, a gas-liquid heat exchanger for heat exchange is provided between the upstream piping line L6 and the downstream piping line L8 of the indoor heat exchanger 5 17 (refrigeration unit 51A) (refer to Fig. 12) example. Fig. 12 is a partial circuit diagram mainly showing a part of the refrigerant circuit of the refrigerating device 51A that is different from the refrigerant circuit of the refrigerating device 51 (see Fig. 1). The gas-liquid heat exchanger 17 is connected between the solenoid valve 11 and the expansion valve 12 with respect to the piping line L6. In addition, it is connected between the internal heat exchanger 5 and the branch portion D3 with respect to the piping line L8.

在冷凍裝置51A的冷卻運轉中，冷媒在第12圖所示的由粗線表示的配管部分中，向箭頭的方向流通。在冷卻運轉中即將進入膨脹閥12的液態冷媒，在此之前，在氣液熱交換器17中與從庫內熱交換器5流出的氣態冷媒進行熱交換而被冷卻，過冷度增大。這樣一來，由於利用庫內熱交換器5中的熱交換，從庫C1內的空氣獲取的熱量增加，因此，使庫C1內冷卻的能力提高。並且，由於可以進一步促進庫內熱交換器5中的液態冷媒的蒸發，因此，可以防止壓縮機1的液擊現象的發生。In the cooling operation of the refrigerating device 51A, the refrigerant circulates in the direction of the arrow in the piping portion indicated by the thick line shown in FIG. 12. The liquid refrigerant that is about to enter the expansion valve 12 during the cooling operation is cooled by heat exchange with the gaseous refrigerant flowing out of the internal heat exchanger 5 in the gas-liquid heat exchanger 17, and the degree of supercooling increases. In this way, since the heat exchange in the internal heat exchanger 5 is used, the amount of heat taken from the air in the compartment C1 is increased, and therefore, the cooling capacity in the compartment C1 is improved. In addition, since the evaporation of the liquid refrigerant in the internal heat exchanger 5 can be further promoted, the occurrence of the liquid hammer phenomenon of the compressor 1 can be prevented.

另一方面，在升溫運轉中，液態冷媒不流通於配管線路L6，而是流通於配管線路L7，因此氣液熱交換器17不產生作用。On the other hand, during the heating operation, the liquid refrigerant does not circulate through the piping line L6 but circulates through the piping line L7, so the gas-liquid heat exchanger 17 does not work.

（變化例2）相對於冷凍裝置51，變化例2具備二個以上的庫內熱交換器（冷凍裝置51B）。此處，參照第13圖，對具備兩個庫內熱交換器25A、25B的例子進行說明。第13圖是主要表示冷凍裝置51B的冷媒回路的與冷凍裝置51的冷媒回路（參照第1圖）不同部分的局部回路圖。(Modification 2) With respect to the freezing device 51, the modification 2 includes two or more indoor heat exchangers (the freezing device 51B). Here, with reference to Fig. 13, an example in which two internal heat exchangers 25A and 25B are provided will be described. FIG. 13 is a partial circuit diagram mainly showing a different part of the refrigerant circuit of the refrigerating device 51B from the refrigerant circuit of the refrigerating device 51 (see FIG. 1).

如第13圖所示，冷凍裝置51B在受液器4與分歧部D3之間，並聯地連接含有風扇FM25A的庫內熱交換器25A與含有風扇FM25B的庫內熱交換器25B。在庫內熱交換器25A的上游側（受液器4側）連接有膨脹閥22A，在庫內熱交換器25B的上游側連接有膨脹閥22B。膨脹閥22A、22B的上游側匯合成一條線路，經由電磁閥23連接於受液器4。在庫內熱交換器25A和膨脹閥22A之間、與受液器4之間，設有電磁閥21A。在庫內熱交換器25B和膨脹閥22B之間、與受液器4之間，設有電磁閥21B。膨脹閥22A、22B的下游側匯合成一條線路，連接於分歧部D3。風扇FM25A和風扇FM25B、以及電磁閥21A和電磁閥21B的動作，根據控制部31而被控制。As shown in FIG. 13, the refrigeration unit 51B is connected in parallel between the receiver 4 and the branch portion D3, and the indoor heat exchanger 25A including the fan FM25A and the indoor heat exchanger 25B including the fan FM25B are connected in parallel. The expansion valve 22A is connected to the upstream side (the receiver 4 side) of the internal heat exchanger 25A, and the expansion valve 22B is connected to the upstream side of the internal heat exchanger 25B. The upstream sides of the expansion valves 22A and 22B merge into a single line, and are connected to the receiver 4 via the solenoid valve 23. A solenoid valve 21A is provided between the internal heat exchanger 25A and the expansion valve 22A and between the liquid receiver 4. A solenoid valve 21B is provided between the internal heat exchanger 25B and the expansion valve 22B and between the liquid receiver 4. The downstream sides of the expansion valves 22A and 22B merge into one line, which is connected to the branch D3. The operations of the fan FM25A and the fan FM25B, and the solenoid valve 21A and the solenoid valve 21B are controlled by the control unit 31.

此冷凍裝置51B，例如載置於具備應該維持恒溫的二個以上的庫的冷凍車。庫內熱交換器25A與庫內熱交換器25B，以對各自不同的庫的內部進行冷卻和升溫的方式設置。This refrigerating device 51B is mounted, for example, in a refrigerating vehicle equipped with two or more compartments that should maintain a constant temperature. The internal heat exchanger 25A and the internal heat exchanger 25B are installed so as to cool and raise the temperature of the inside of the respective different compartments.

電磁閥的數量和位置等，並非限定於第13圖所示的例子。The number and position of solenoid valves are not limited to the example shown in Fig. 13.

根據此變化例2，可以利用組合各電磁閥21A、21B、23的打開狀態與關閉狀態，分別獨立地進行二個以上的庫的冷卻或升溫。例如，可以只將特定的一個或特定的二個以上的庫冷卻、或將全部的庫加以冷卻等。According to this modification 2, the open state and the closed state of the solenoid valves 21A, 21B, and 23 can be combined to independently cool or raise the temperature of two or more compartments. For example, it is possible to cool only a specific one or two or more specific compartments, or to cool all the compartments.

可以使變化例1與變化例2適當地組合。Modification 1 and Modification 2 can be appropriately combined.

流通方向限制部RK並非限定於使用二個以上的止回閥而構成，但根據使用止回閥，可以利用較低的成本來構成流通方向限制部RK。The flow direction restricting portion RK is not limited to the use of two or more check valves. However, depending on the use of check valves, the flow direction restricting portion RK can be constructed at a relatively low cost.

（變化例3）在變化例3中，使冷凍裝置51成為冷凍裝置57，該冷凍裝置57具有不具備流通方向限制部RK且可以進行冷卻運轉和升溫運轉的冷媒回路。冷凍裝置57的構成，表示於此冷媒回路圖也就是第14圖和表示控制系統的第15圖中。亦即，相對於冷凍裝置51的冷媒回路，冷凍裝置57的冷媒回路刪掉流通方向限制部RK，並且使並聯回路LP2成為將電磁閥11和電磁閥13分別替換為止回閥71和止回閥73而成的並聯回路LP72。除此以外的構成相同。(Modification 3) In Modification 3, the refrigerating device 51 is made into a refrigerating device 57 having a refrigerant circuit that does not include the flow direction restricting portion RK and can perform a cooling operation and a temperature-rising operation. The configuration of the refrigerating device 57 is shown in Fig. 14 which is the refrigerant circuit diagram and Fig. 15 which shows the control system. That is, with respect to the refrigerant circuit of the refrigeration device 51, the refrigerant circuit of the refrigeration device 57 deletes the flow direction restricting portion RK, and makes the parallel circuit LP2 replace the solenoid valve 11 and the solenoid valve 13 with the check valve 71 and the check valve, respectively 73 made up of parallel loop LP72. The other configurations are the same.

此構成由於不具備流通方向限制部RK，因此，流通於庫內熱交換器5中的冷媒的方向，在冷卻運轉與升溫運轉中相反。亦即，在並聯回路LP72中，當冷媒從受液器4流入庫內熱交換器5時，流通於配管線路L76；而當冷媒從庫內熱交換器5向受液器4流通時，流通於配管線路L77。Since this configuration does not include the flow direction restricting portion RK, the direction of the refrigerant flowing in the indoor heat exchanger 5 is reversed during the cooling operation and the temperature increase operation. That is, in the parallel circuit LP72, when the refrigerant flows from the receiver 4 into the internal heat exchanger 5, it circulates through the piping line L76; and when the refrigerant circulates from the internal heat exchanger 5 to the receiver 4, it circulates through the piping Line L77.

關於此冷凍裝置57的冷卻運轉和升溫運轉，主要參照第16圖～第18圖來進行說明。第16圖是用以說明冷卻運轉時的冷媒回路的圖。第17圖是用以說明升溫運轉時的冷媒回路的圖。第18圖是用以說明各運轉時的控制部31的控制的表格。第17圖和第18圖，與第9圖和第10圖相同地，將冷媒流動的配管部位以粗線表示，將冷媒的流動方向沿著配管以箭頭表示。The cooling operation and the heating operation of the refrigeration device 57 will be mainly described with reference to FIGS. 16 to 18. Fig. 16 is a diagram for explaining the refrigerant circuit during the cooling operation. Fig. 17 is a diagram for explaining the refrigerant circuit during the heating operation. Fig. 18 is a table for explaining the control of the control unit 31 during each operation. In Figs. 17 and 18, similar to Figs. 9 and 10, the piping portion where the refrigerant flows is indicated by thick lines, and the flow direction of the refrigerant is indicated by arrows along the piping.

（冷卻運轉）如第18圖的表格所示，在冷凍裝置57的冷卻運轉中，控制部31使四通閥2為模式A，風扇FM1和風扇FM2為運轉狀態。此冷卻運轉中的由風扇FM1和風扇FM2所產生的送風方向，在第16圖中，分別以箭頭DR71和箭頭DR72表示。從庫外熱交換器3的埠3Ba至埠3Aa的冷媒的相態、和庫外熱交換器3的作用，與冷凍裝置51的冷卻運轉相同。亦即，在冷凍裝置57的冷卻運轉中，庫外熱交換器3的第2庫外熱交換器3B與第1庫外熱交換器3A，一體地作為冷凝器而發揮功能。這樣一來，氣態冷媒對於外部空氣散熱而冷凝，以高壓液態冷媒的形式從埠3Aa流入配管線路L5。(Cooling operation) As shown in the table of FIG. 18, in the cooling operation of the refrigeration device 57, the control unit 31 sets the four-way valve 2 to mode A, and the fan FM1 and the fan FM2 are in the operating state. The blowing directions generated by the fan FM1 and the fan FM2 during this cooling operation are indicated by the arrow DR71 and the arrow DR72 in Fig. 16, respectively. The phase state of the refrigerant from the port 3Ba to the port 3Aa of the external heat exchanger 3 and the function of the external heat exchanger 3 are the same as the cooling operation of the refrigerating device 51. That is, in the cooling operation of the refrigerating device 57, the second external heat exchanger 3B of the external heat exchanger 3 and the first external heat exchanger 3A function as a condenser integrally. In this way, the gaseous refrigerant dissipates heat to the outside air and condenses, and flows into the piping line L5 from the port 3Aa in the form of a high-pressure liquid refrigerant.

流入配管線路L5中的冷媒，在高壓下大致全部成為液相。此液態冷媒，流經受液器4而流入並聯回路LP72。在並聯回路LP72中，只允許液態冷媒根據止回閥71而朝向配管線路L76流入，並進入膨脹閥72。在膨脹閥72中，液態冷媒膨脹。這樣一來，液態冷媒由於壓力和溫度降低，氣化被促進，而成為氣相與液相混合的氣液混合冷媒。從膨脹閥72流出的氣液混合冷媒，流入庫內熱交換器5。Almost all of the refrigerant flowing into the piping line L5 becomes a liquid phase under high pressure. This liquid refrigerant flows through the receiver 4 and flows into the parallel circuit LP72. In the parallel circuit LP72, only the liquid refrigerant is allowed to flow into the piping line L76 via the check valve 71 and enter the expansion valve 72. In the expansion valve 72, the liquid refrigerant expands. In this way, the liquid refrigerant is reduced in pressure and temperature, and gasification is promoted, and it becomes a gas-liquid mixed refrigerant in which the gas phase and the liquid phase are mixed. The gas-liquid mixed refrigerant flowing out of the expansion valve 72 flows into the internal heat exchanger 5.

在庫內熱交換器5中，風扇FM2根據控制部31的控制而處於運轉狀態，使庫C1內的空氣向第16圖的箭頭DR72的方向流動。在此狀態下，氣液混合冷媒與庫C1內的空氣進行熱交換，從庫C1內的空氣獲取熱量，完全地氣化而成為氣態冷媒。亦即，庫內熱交換器5作為蒸發器而發揮功能，庫C1內被冷卻。In the internal heat exchanger 5, the fan FM2 is in an operating state under the control of the control unit 31, and causes the air in the compartment C1 to flow in the direction of the arrow DR72 in Fig. 16. In this state, the gas-liquid mixed refrigerant exchanges heat with the air in the storage C1, obtains heat from the air in the storage C1, and is completely vaporized to become a gaseous refrigerant. That is, the internal heat exchanger 5 functions as an evaporator, and the inside of the storage C1 is cooled.

從庫內熱交換器5流出的氣態冷媒流入配管線路L8。在冷凍裝置57中，配管線路L8將庫內熱交換器5與四通閥2的埠2d之間不分歧地連接。因此，氣態冷媒從成為模式A的四通閥2的埠2d，流經埠2c，進一步，流經蓄液器6並返回至壓縮機1的吸入口。The gaseous refrigerant flowing out of the internal heat exchanger 5 flows into the piping line L8. In the refrigerating device 57, the piping line L8 connects the internal heat exchanger 5 and the port 2d of the four-way valve 2 without branching. Therefore, the gaseous refrigerant flows from the port 2d of the four-way valve 2 of the mode A through the port 2c, and further flows through the accumulator 6 and returns to the suction port of the compressor 1.

（升溫運轉）如第18圖的表格所示，在冷凍機57的升溫運轉中，控制部31使四通閥2為模式B，風扇FM1和風扇FM2為運轉狀態。此升溫運轉中的由風扇FM1和風扇FM2所產生的送風方向與冷卻運轉相同，為一定的方向，在第17圖中分別以箭頭DR73和箭頭DR74表示。(Temperature Warming Operation) As shown in the table of FIG. 18, during the temperature raising operation of the refrigerator 57, the control unit 31 sets the four-way valve 2 to mode B, and the fan FM1 and the fan FM2 are in the operating state. The blowing direction generated by the fan FM1 and the fan FM2 during the heating operation is the same as the cooling operation, and is a constant direction, and is indicated by an arrow DR73 and an arrow DR74 in FIG. 17, respectively.

如第17圖所示，根據控制部31的控制，由壓縮機1的吐出口吐出的高壓氣態冷媒，從成為模式B的四通閥2的埠2a，經過埠2d，流入配管線路L8。在冷凍裝置57中，如上所述，配管線路L8將四通閥2的埠2d與庫內熱交換器5之間無分歧地連接。因此，氣態冷媒流入庫內熱交換器5的方向，與在冷卻運轉時流入庫內熱交換器5的方向相反。As shown in FIG. 17, under the control of the control unit 31, the high-pressure gaseous refrigerant discharged from the discharge port of the compressor 1 flows from the port 2a of the four-way valve 2 in the mode B through the port 2d, and flows into the piping line L8. In the refrigerating device 57, as described above, the piping line L8 connects the port 2d of the four-way valve 2 and the internal heat exchanger 5 without any branch. Therefore, the direction in which the gaseous refrigerant flows into the internal heat exchanger 5 is opposite to the direction in which it flows into the internal heat exchanger 5 during the cooling operation.

在庫內熱交換器5中，如上所述，根據控制部31的控制，風扇FM2處於運轉狀態，庫C1內的空氣向第17圖的箭頭DR74方向流動。在此狀態下，氣態冷媒與庫C1內的空氣進行熱交換，向庫C1內的空氣中放出熱量，進行冷凝，大致成為高壓液態冷媒。因此，庫C1內被升溫。In the internal heat exchanger 5, as described above, according to the control of the control unit 31, the fan FM2 is in the operating state, and the air in the compartment C1 flows in the direction of the arrow DR74 in FIG. 17. In this state, the gaseous refrigerant exchanges heat with the air in the storage C1, releases heat to the air in the storage C1, condenses, and substantially becomes a high-pressure liquid refrigerant. Therefore, the temperature in the bank C1 is increased.

從庫內熱交換器5流出的液態冷媒，流經並聯回路LP72的具有止回閥73的配管線路L77和受液器4，通過配管線路L5從埠3Aa流入庫外熱交換器3的第1庫外熱交換器3A。The liquid refrigerant flowing out of the internal heat exchanger 5 flows through the piping line L77 with the check valve 73 of the parallel circuit LP72 and the receiver 4, and flows from the port 3Aa into the first reservoir of the external heat exchanger 3 through the piping line L5. External heat exchanger 3A.

在庫外熱交換器3中，根據控制部31的控制，風扇FM1處於運轉狀態，外部空氣向第17圖的箭頭DR73方向流動。因此，第1庫外熱交換器3A相對於第2庫外熱交換器3B，位於外部空氣的流通的上游側。在此狀態下，在第1庫外熱交換器3A內，液態冷媒被冷卻，溫度下降。亦即，第1庫外熱交換器3A對於液態冷媒，作為過冷卻熱交換器而發揮功能。與液態冷媒一同流入第1庫外熱交換器3A中的氣態冷媒，也根據此冷卻而大致全部成為液態冷媒。In the external heat exchanger 3, under the control of the control unit 31, the fan FM1 is in the operating state, and the outside air flows in the direction of the arrow DR73 in FIG. 17. Therefore, the first external heat exchanger 3A is located on the upstream side of the flow of outside air with respect to the second external heat exchanger 3B. In this state, the liquid refrigerant is cooled in the first external heat exchanger 3A, and the temperature drops. That is, the first external heat exchanger 3A functions as a supercooling heat exchanger for the liquid refrigerant. The gaseous refrigerant flowing into the first external heat exchanger 3A together with the liquid refrigerant is also cooled by this and almost all becomes the liquid refrigerant.

過冷卻後的液態冷媒，從第1庫外熱交換器3A的埠3Ab流出，並流入配管線路L3。在配管線路L3中，液態冷媒經由止回閥8而進入膨脹閥7。在膨脹閥7中，液態冷媒膨脹。這樣一來，液態冷媒由於壓力和溫度降低，氣化被促進，而成為氣相與液相混合的氣液混合冷媒。從膨脹閥7流出的氣液混合冷媒，從埠3Bb流入第2庫外熱交換器3B。在第2庫外熱交換器3B中，從埠3Bb流入的氣液混合冷媒，利用與外部空氣的熱交換從外部空氣獲取熱量而蒸發，成為氣態冷媒，從埠3Ba流入配管線路L2。亦即，第2庫外熱交換器3B作為蒸發器而發揮功能。流入配管線路L2中的氣態冷媒，從成為模式B的四通閥2的埠2b經過埠2c，流經蓄液器6並返回至壓縮機1的吸入口。The supercooled liquid refrigerant flows out of the port 3Ab of the first external heat exchanger 3A, and flows into the piping line L3. In the piping line L3, the liquid refrigerant enters the expansion valve 7 via the check valve 8. In the expansion valve 7, the liquid refrigerant expands. In this way, the liquid refrigerant is reduced in pressure and temperature, and gasification is promoted, and it becomes a gas-liquid mixed refrigerant in which the gas phase and the liquid phase are mixed. The gas-liquid mixed refrigerant flowing out of the expansion valve 7 flows into the second external heat exchanger 3B from the port 3Bb. In the second external heat exchanger 3B, the gas-liquid mixed refrigerant flowing in from the port 3Bb obtains heat from the outside air by heat exchange with the outside air, evaporates, becomes a gaseous refrigerant, and flows into the piping line L2 from the port 3Ba. That is, the second external heat exchanger 3B functions as an evaporator. The gaseous refrigerant flowing into the piping line L2 passes through the port 2b of the four-way valve 2 in the mode B, passes through the port 2c, flows through the accumulator 6 and returns to the suction port of the compressor 1.

接著，對冷凍裝置57的除霜運轉進行說明。Next, the defrosting operation of the refrigerating device 57 will be described.

（庫內熱交換器5的除霜運轉）即便在冷凍裝置57中，如果長時間進行冷卻運轉，庫C1內的空氣中所含有的水分也可能會結冰成霜，並附著於庫內熱交換器5的散熱片上。由於散熱片上的結霜會阻礙熱交換，因此，實行庫內熱交換器5的除霜運轉以便除霜。如第18圖的表格所示，此除霜運轉，只有在使風扇FM1和風扇FM2停止方面，不同於升溫運轉。(Defrosting operation of the internal heat exchanger 5) Even in the refrigeration unit 57, if the cooling operation is performed for a long time, the moisture contained in the air in the storage C1 may freeze into frost and adhere to the internal heat exchanger 5 on the heat sink. Since frost on the radiating fins hinders heat exchange, the defrosting operation of the internal heat exchanger 5 is performed to defrost. As shown in the table in Fig. 18, this defrosting operation differs from the heating operation only in stopping the fan FM1 and the fan FM2.

（庫外熱交換器3的除霜運轉）即便在冷凍裝置57中，如果長時間進行升溫運轉，外部空氣中所含有的水分也可能會結冰成霜，並附著於庫外熱交換器3的散熱片3f上。在冷凍裝置57中，庫外熱交換器3的作用與冷凍裝置51相同。因此，庫外熱交換器3的散熱片3f上的積雪或結霜極其不易產生。但是，當使冷凍車C在降雪時行車時，如果降雪量明顯較多，庫外熱交換器3的上風側（第1庫外熱交換器3A側）的鄰接的散熱片3f之間也可能會堵塞。此時，由於熱交換受到阻礙，不能作為熱交換器而發揮功能，因此，實行庫外熱交換器3的除霜運轉，對散熱片3f進行融雪和除霜。如第18圖的表格所示，此除霜運轉，只有在使風扇FM1和風扇FM2停止方面，不同於冷卻運轉。(Defrosting operation of the external heat exchanger 3) Even in the refrigeration unit 57, if the temperature increase operation is performed for a long time, the moisture contained in the outside air may freeze and become frost and adhere to the external heat exchanger 3 On the heat sink 3f. In the freezing device 57, the function of the external heat exchanger 3 is the same as that of the freezing device 51. Therefore, the accumulation of snow or frost on the fins 3f of the external heat exchanger 3 is extremely unlikely to occur. However, when the refrigerated vehicle C is driven during snowfall, if the amount of snowfall is significantly greater, the adjacent fins 3f on the windward side of the external heat exchanger 3 (the first external heat exchanger 3A side) will also be spaced between the adjacent fins 3f. It may be clogged. At this time, since the heat exchange is hindered and cannot function as a heat exchanger, the defrosting operation of the external heat exchanger 3 is performed to melt snow and defrost the fins 3f. As shown in the table in Figure 18, this defrosting operation differs from the cooling operation only in stopping the fan FM1 and the fan FM2.

冷凍裝置57尤其是在升溫運轉中，獲得以下效果。In particular, the refrigerating device 57 obtains the following effects during the heating operation.

在第2庫外熱交換器3B中，氣液混合冷媒進行從外部空氣獲取熱量的熱交換，成為低壓氣態冷媒。在庫外熱交換器3中，多個散熱片3f以橫跨於第1庫外熱交換器3A與第2庫外熱交換器3B的方式設置。因此，在第1庫外熱交換器3A中，液態冷媒所放出的部分熱量傳遞至散熱片3f並移動至第2庫外熱交換器3B，作為在第2庫外熱交換器3B中的相變化的蒸發熱而被利用。這樣一來，由於第2庫外熱交換器3B中的液態冷媒的蒸發得以被促進，因此，可以防止液態冷媒被吸入至壓縮機1，也就是所謂的液擊現象的產生。In the second external heat exchanger 3B, the gas-liquid mixed refrigerant performs heat exchange to obtain heat from the outside air, and becomes a low-pressure gas refrigerant. In the external heat exchanger 3, a plurality of fins 3f are provided so as to straddle the first external heat exchanger 3A and the second external heat exchanger 3B. Therefore, in the first external heat exchanger 3A, part of the heat released by the liquid refrigerant is transferred to the fins 3f and moved to the second external heat exchanger 3B as the phase in the second external heat exchanger 3B. The changed heat of evaporation is utilized. In this way, since the evaporation of the liquid refrigerant in the second external heat exchanger 3B is promoted, it is possible to prevent the liquid refrigerant from being sucked into the compressor 1, which is the so-called liquid hammer phenomenon.

並且，即便運轉環境為例如在寒冷地區中的行車，因降雪而使散熱片3f上積雪時，附著於散熱片3f上的雪，也會因散熱片3f受到第1庫外熱交換器隨著升溫運轉而進行的熱交換所放出的熱量而變得溫熱，從而融化。並且，多個散熱片3f各自在第2庫外熱交換器3B側的部分，由於以下原因而變得溫熱：因利用在第1庫外熱交換器3A的熱交換而被升溫的外部空氣，向下游側流通；及，利用在第1庫外熱交換器3A中的熱交換賦予散熱片3f的熱量，向散熱片3f的下游側傳遞。這樣一來，由於全部散熱片3f均高效率地變暖，因此，極為有效地防止散熱片3f上的積雪或結霜。因此，冷凍裝置57的除霜動作的實行間隔變長，動作效率提高。In addition, even if the operating environment is, for example, driving in a cold area, when snow accumulates on the fins 3f due to snowfall, the snow adhering to the fins 3f will be affected by the first external heat exchanger due to the fins 3f. The heat released by the heat exchange during the heating operation becomes warm and melts. In addition, the portion of each of the plurality of fins 3f on the side of the second external heat exchanger 3B becomes warm due to the following reason: the outside air heated by the heat exchange in the first external heat exchanger 3A , Circulates to the downstream side; and, the heat imparted to the fin 3f by heat exchange in the first external heat exchanger 3A is transferred to the downstream side of the fin 3f. In this way, since all the heat sinks 3f are warmed efficiently, it is extremely effective to prevent snow or frost on the heat sinks 3f. Therefore, the execution interval of the defrosting operation of the refrigerating device 57 becomes longer, and the operation efficiency is improved.

並且，第1庫外熱交換器3A具有二個以上的路徑P1、P2，各路徑按照以下方式配置，亦即，在送風方向（前後方向）上大致不重疊，在吸入面上成為實質獨立的區域。這樣一來，由於吸入面的表面溫度的不均得以被抑制，因此，附著於散熱片3f上的雪均勻地融化。In addition, the first external heat exchanger 3A has two or more paths P1 and P2, and each path is arranged in such a way that it does not substantially overlap in the air blowing direction (front-to-rear direction) and becomes substantially independent on the suction surface area. In this way, since the unevenness of the surface temperature of the suction surface is suppressed, the snow adhering to the heat sink 3f is uniformly melted.

（變化例4）連接第1庫外熱交換器3A的埠3Ab與第2庫外熱交換器3B的埠3Bb的並聯回路LP1（參照第1圖、第4圖、第9圖及第10圖），作為變化例4，也可以替換成沒有止回閥8的並聯回路LP1a。　第19圖中，表示出此並聯回路LP1a。(Modification 4) The parallel circuit LP1 connecting the port 3Ab of the first external heat exchanger 3A and the port 3Bb of the second external heat exchanger 3B (refer to Figures 1, 4, 9 and 10 ), as Modification 4, it can also be replaced with a parallel circuit LP1a without the check valve 8.　 Figure 19 shows this parallel circuit LP1a.

（其他變化例）庫外熱交換器3和庫內熱交換器5中的至少一者，並非限定於上述的鰭管式熱交換器。也可以是例如蛇管式(serpentine)或並流式(parallel flow)，此時也將會獲得相同的效果。針對庫外熱交換器3並非鰭管式熱交換器的情況，詳細地進行說明。首先，準備兩個蛇管式或並流式的熱交換器，在前後方向上並列設置。而且，分別連結冷媒配管，使其中一個熱交換器作為第1庫外熱交換器3A，並且另一熱交換器作為第2庫外熱交換器3B而發揮功能。進一步，將多個熱交換散熱片分別相對於兩個熱交換器的冷媒配管以橫跨的方式而安裝，使兩個熱交換器一體化。(Other modification examples) At least one of the external heat exchanger 3 and the internal heat exchanger 5 is not limited to the above-mentioned fin-and-tube heat exchanger. It can also be serpentine or parallel flow, and the same effect will be obtained in this case. The case where the external heat exchanger 3 is not a fin-tube heat exchanger will be described in detail. First, prepare two serpentine or parallel-flow heat exchangers, which are arranged side by side in the front-rear direction. Furthermore, the refrigerant pipes are respectively connected so that one of the heat exchangers functions as the first external heat exchanger 3A, and the other heat exchanger functions as the second external heat exchanger 3B. Furthermore, a plurality of heat exchange fins are respectively installed across the refrigerant pipes of the two heat exchangers to integrate the two heat exchangers.

上述的實施例和各變化例，也可以盡可能組合而實施。例如，可以使變化例1與變化例3組合，並將氣液熱交換器17應用於冷凍裝置57。此時，冷媒回路的第12圖所表示的部分中，將電磁閥11替換為止回閥71，將電磁閥13替換為止回閥73。The above-mentioned embodiments and various modified examples can also be implemented in combination as much as possible. For example, it is possible to combine Modification 1 and Modification 3, and apply the gas-liquid heat exchanger 17 to the refrigeration device 57. At this time, in the portion shown in FIG. 12 of the refrigerant circuit, the solenoid valve 11 is replaced with the check valve 71, and the solenoid valve 13 is replaced with the check valve 73.

1‧‧‧壓縮機2‧‧‧四通閥2a～2d‧‧‧埠3‧‧‧庫外熱交換器3A‧‧‧第1庫外熱交換器3Aa、3Ab‧‧‧埠3B‧‧‧第2庫外熱交換器3Ba、3Bb‧‧‧埠3C‧‧‧管3f‧‧‧散熱片3LA、3LB‧‧‧冷媒配管線路4‧‧‧受液器5、25A、25B‧‧‧庫內熱交換器6‧‧‧蓄液器7、12、22A、22B、72‧‧‧膨脹閥8～10、14～16、71、73‧‧‧止回閥11、13、21A、21B、23‧‧‧電磁閥17‧‧‧氣液熱交換器31‧‧‧控制部32‧‧‧輸入部51、51A、51B、57‧‧‧冷凍裝置C‧‧‧冷凍車C1‧‧‧庫（貨櫃）CV‧‧‧內部空間D1～D4‧‧‧分歧部G、GA1、GA2、GB3～GB5‧‧‧配管列群FM1、FM2、FM25A、FM25B‧‧‧風扇（送風機）LP1、LP2、LP72、LP1A‧‧‧並聯回路L1～L11、3LA、3LB、L76、L77‧‧‧配管線路Na、Nb‧‧‧路徑數P1～P5‧‧‧路徑Qa、Qb‧‧‧容量RA、RB‧‧‧流路RK‧‧‧流通方向限制部S‧‧‧收容體1‧‧‧Compressor 2‧‧‧Four-way valve 2a～2d‧‧‧Port 3‧‧‧External heat exchanger 3A‧‧‧The first external heat exchanger 3Aa, 3Ab‧‧‧Port 3B‧‧ ‧The second external heat exchanger 3Ba, 3Bb‧‧‧Port 3C‧‧‧Tube 3f‧‧‧Radiating fins 3LA, 3LB‧‧‧Refrigerant piping line 4‧‧‧Acceptor 5, 25A, 25B‧‧‧ Internal heat exchanger 6‧‧‧Accumulator 7,12,22A,22B,72‧‧‧Expansion valve 8～10,14～16,71,73‧‧‧Check valve 11,13,21A,21B, 23‧‧‧Solenoid valve 17‧‧‧Gas-liquid heat exchanger 31‧‧‧Control unit 32‧‧‧Input unit 51, 51A, 51B, 57‧‧‧Refrigeration device C‧‧‧Refrigerator car C1‧‧‧Storage (Container) CV‧‧‧Internal space D1～D4‧‧‧Branch G, GA1, GA2, GB3～GB5‧‧‧Piping train group FM1, FM2, FM25A, FM25B‧‧‧Fan (blower) LP1, LP2 LP72, LP1A‧‧‧Parallel circuit L1～L11, 3LA, 3LB, L76, L77‧‧‧Pipe line Na, Nb‧‧‧Number of paths P1～P5‧‧‧Path Qa, Qb‧‧‧Capacity RA, RB‧ ‧‧Flow Path RK‧‧‧Circulation Direction Restriction Section S‧‧‧Container

第1圖是本發明的冷凍裝置用熱交換器及冷凍裝置的實施例也就是庫外熱交換器3與使用此庫外熱交換器3的冷凍裝置51的冷媒回路圖。第2圖是用以說明冷凍裝置51的控制系統的圖。第3圖是用以說明冷凍裝置51中的四通閥2、電磁閥11及電磁閥13的控制模式的圖。第4圖是用以說明冷凍裝置51中的庫外熱交換器3的示意性剖面圖。第5圖是用以說明庫外熱交換器3的第1立體圖。第6圖是用以說明庫外熱交換器3的第2立體圖。第7圖是用以說明庫外熱交換器3內的路徑的圖。第8圖是用以說明冷凍裝置51的載置例也就是冷凍車C的側視圖。第9圖是用以說明冷凍裝置51的冷卻運轉的冷媒回路圖。第10圖是用以說明冷凍裝置51的升溫運轉的冷媒回路圖。第11圖是用以說明冷凍裝置51中的控制部31所進行的控制的表格。第12圖是用以說明變化例1也就是冷凍裝置51A中的冷媒回路的主要部分的局部冷媒回路圖。第13圖是用以說明變化例2也就是冷凍裝置51B中的冷媒回路的主要部分的局部冷媒回路圖。第14圖是變化例3也就是冷凍裝置57中的冷媒回路圖。第15圖是用以說明冷凍裝置57的控制系統的圖。第16圖是用以說明冷凍裝置57的冷卻運轉的冷媒回路圖。第17圖是用以說明冷凍裝置57的升溫運轉的冷媒回路圖。第18圖是用以說明冷凍裝置57中的控制部31所進行的控制的表格。第19圖是用以說明變化例4的並聯回路LP1a的圖。Fig. 1 is an example of a heat exchanger for a refrigeration system and a refrigeration system according to the present invention, that is, a refrigerant circuit diagram of an external heat exchanger 3 and a refrigeration system 51 using the external heat exchanger 3. FIG. 2 is a diagram for explaining the control system of the refrigeration device 51. As shown in FIG. FIG. 3 is a diagram for explaining the control modes of the four-way valve 2, the solenoid valve 11, and the solenoid valve 13 in the refrigeration system 51. As shown in FIG. FIG. 4 is a schematic cross-sectional view for explaining the external heat exchanger 3 in the refrigeration unit 51. As shown in FIG. FIG. 5 is a first perspective view for explaining the external heat exchanger 3. FIG. 6 is a second perspective view for explaining the external heat exchanger 3. FIG. 7 is a diagram for explaining the path in the external heat exchanger 3. Fig. 8 is a side view of the refrigerating vehicle C, which is an example of the placement of the refrigerating device 51. FIG. 9 is a refrigerant circuit diagram for explaining the cooling operation of the refrigerating device 51. As shown in FIG. Fig. 10 is a refrigerant circuit diagram for explaining the temperature-raising operation of the refrigerating device 51. FIG. 11 is a table for explaining the control performed by the control unit 31 in the refrigeration system 51. As shown in FIG. Fig. 12 is a partial refrigerant circuit diagram for explaining the main part of the refrigerant circuit in the refrigeration system 51A in Modification 1. Fig. 13 is a local refrigerant circuit diagram for explaining the main part of the refrigerant circuit in the refrigeration system 51B in Modification 2. Fig. 14 is a circuit diagram of the refrigerant circuit in the refrigerating system 57, which is the third modification. Fig. 15 is a diagram for explaining the control system of the refrigerating device 57. Fig. 16 is a refrigerant circuit diagram for explaining the cooling operation of the refrigeration unit 57. Fig. 17 is a refrigerant circuit diagram for explaining the temperature-raising operation of the refrigeration unit 57. FIG. 18 is a table for explaining the control performed by the control unit 31 in the refrigeration system 57. Fig. 19 is a diagram for explaining the parallel circuit LP1a of Modification 4.

國內寄存資訊 (請依寄存機構、日期、號碼順序註記) 無Domestic hosting information (please note in the order of hosting organization, date, and number) None

國外寄存資訊 (請依寄存國家、機構、日期、號碼順序註記) 無Foreign hosting information (please note in the order of hosting country, institution, date, and number) None

3‧‧‧庫外熱交換器 3‧‧‧External heat exchanger

3A‧‧‧第1庫外熱交換器 3A‧‧‧The first external heat exchanger

3Aa、3Ab‧‧‧埠 3Aa、3Ab‧‧‧Port

3B‧‧‧第2庫外熱交換器 3B‧‧‧The second external heat exchanger

3Ba、3Bb‧‧‧埠 3Ba, 3Bb‧‧‧Port

3C‧‧‧管 3C‧‧‧Tube

3LA、3LB‧‧‧冷媒配管線路 3LA, 3LB‧‧‧Refrigerant Piping Line

7‧‧‧膨脹閥 7‧‧‧Expansion valve

8、9‧‧‧止回閥 8,9‧‧‧Check valve

GA1、GA2、GB3~GB5‧‧‧配管列群 GA1, GA2, GB3~GB5‧‧‧Piping array group

FM1‧‧‧風扇(送風機) FM1‧‧‧Fan (blower)

LP1‧‧‧並聯回路 LP1‧‧‧Parallel circuit

L2、L3、L4、L9‧‧‧配管線路 L2, L3, L4, L9‧‧‧Piping line

P1~P5‧‧‧路徑 P1~P5‧‧‧Path

Claims

一種冷凍裝置用熱交換器，其為鰭管式的冷凍裝置用熱交換器，用來作為冷凍裝置的庫外熱交換器，其中該冷凍裝置具備冷媒回路，該冷媒回路包括庫內熱交換器和前述庫外熱交換器，且該冷凍裝置能夠選擇性地進行使庫內冷卻的冷卻運轉與使庫內升溫的升溫運轉，該冷凍裝置用熱交換器具備：第1熱交換器，其具有第1冷媒配管線路；第2熱交換器，其具有串聯連接於前述第1冷媒配管線路的第2冷媒配管線路，且與前述第1熱交換器並列設置；複數個散熱片，其跨設且連結於前述第1冷媒配管線路與前述第2冷媒配管線路的兩方；及，送風機，其對前述第1熱交換器和前述第2熱交換器送風；並且，在前述送風機的送風方向中，前述第1冷媒配管線路為1列，且前述第2冷媒配管線路的配管具有複數列；前述第1冷媒配管線路的配管和前述第2冷媒配管線路的配管，以正交貫穿前述第1熱交換器和前述第2熱交換器各自的散熱片的方式連結；前述第1冷媒配管線路具有複數條路徑，路徑數為 Na，且Na為2以上的整數，前述第2冷媒配管線路具有複數條路徑，路徑數為Nb，且Nb為3以上的整數，前述路徑數Na與前述路徑數Nb，滿足2

Na<Nb；前述第1冷媒配管線路的複數條路徑，在一端與另一端之間為並聯地連接，且在前述第1熱交換器的吸入面上被配置成實質獨立的區域；前述第2冷媒配管線路的複數條路徑，在一端與另一端之間以完全流體獨立的方式並聯地連接，且在由前述送風機所產生的送風方向中彼此不重疊，並在前述第2熱交換器的吸入面上被配置成實質獨立的區域；前述第2冷媒配管線路的各路徑，以經由前述第2熱交換器的複數列的全部列的方式來被配置；在前述送風機所產生的送風中，以使前述第1熱交換器成為上游側，且使前述第2熱交換器成為下游側的方式並列設置；在前述冷卻運轉中，在前述第2熱交換器中使氣狀冷媒冷凝後，在前述第1熱交換器中使前述第2熱交換器中未冷凝的前述氣狀冷媒冷凝，並且使流通於前述第1冷媒配管線路的配管的已冷凝的冷媒的速度大於流通於前述第2冷媒配管線路的配管的已冷凝的冷媒的速度，以增加冷媒的過冷度；在前述升溫運轉中，在前述第1熱交換器中使液狀冷媒的過冷度增加後，作為蒸發器來發揮功能而在前述第2熱交換器中使液狀冷媒蒸發，並且經由前述複數個散熱片自前述第1熱交換器將熱量傳遞至前述第2熱交換器。 A heat exchanger for a refrigeration device, which is a fin-tube type heat exchanger for a refrigeration device, used as an external heat exchanger of the refrigeration device, wherein the refrigeration device is provided with a refrigerant circuit, and the refrigerant circuit includes an internal heat exchanger and The aforementioned external heat exchanger, and the refrigeration device can selectively perform a cooling operation to cool the interior and a temperature increase operation to raise the temperature in the interior, and the heat exchanger for a refrigeration device includes: a first heat exchanger having a first heat exchanger 1 refrigerant piping line; second heat exchanger, which has a second refrigerant piping line connected in series to the first refrigerant piping line, and is arranged in parallel with the first heat exchanger; a plurality of radiating fins, which are arranged across and connected On both sides of the first refrigerant piping line and the second refrigerant piping line; and, a blower that blows air to the first heat exchanger and the second heat exchanger; and, in the blowing direction of the blower, The first refrigerant piping line has one row, and the piping of the second refrigerant piping line has multiple rows; the piping of the first refrigerant piping line and the piping of the second refrigerant piping line pass through the first heat exchanger orthogonally It is connected to the respective fins of the second heat exchanger; the first refrigerant piping line has a plurality of paths, the number of paths is Na, and Na is an integer of 2 or more, and the second refrigerant piping line has a plurality of paths, The number of paths is Nb, and Nb is an integer greater than or equal to 3, the aforementioned number of paths Na and the aforementioned number of paths Nb satisfy 2

Na<Nb; the plural paths of the first refrigerant piping line are connected in parallel between one end and the other end, and are arranged as substantially independent areas on the suction surface of the first heat exchanger; The multiple paths of the refrigerant piping line are connected in parallel in a completely fluid-independent manner between one end and the other end, and do not overlap each other in the blowing direction generated by the blower, and are sucked in by the second heat exchanger The surface is arranged as a substantially independent area; each path of the second refrigerant piping line is arranged to pass through all the rows of the plurality of rows of the second heat exchanger; in the air flow generated by the air blower, The first heat exchanger is placed on the upstream side and the second heat exchanger is placed on the downstream side. In the cooling operation, the gaseous refrigerant is condensed in the second heat exchanger, and then the gas refrigerant is condensed in the second heat exchanger. In the first heat exchanger, the gaseous refrigerant that is not condensed in the second heat exchanger is condensed, and the speed of the condensed refrigerant flowing through the piping of the first refrigerant piping line is greater than that of the second refrigerant piping The speed of the condensed refrigerant in the piping of the circuit increases the degree of subcooling of the refrigerant; in the heating operation, the degree of subcooling of the liquid refrigerant is increased in the first heat exchanger, and it functions as an evaporator In the second heat exchanger, the liquid refrigerant is evaporated, and heat is transferred from the first heat exchanger to the second heat exchanger via the plurality of fins.

如請求項1所述的冷凍裝置用熱交換器，其中在前述第1冷媒配管線路與前述第2冷媒配管線路之間具備膨脹閥，該膨脹閥僅在使前述冷媒自前述第1冷媒配管線路流至前述第2冷媒配管線路的前述升溫運轉中發揮功能。 The heat exchanger for a refrigeration system according to claim 1, wherein an expansion valve is provided between the first refrigerant piping line and the second refrigerant piping line, and the expansion valve is only used to allow the refrigerant to flow from the first refrigerant piping line. It functions during the temperature increase operation that flows to the second refrigerant piping line.