562916 A7 ---^-- 五、發明說明（π 【發明領域】 本發明有關於一種冷凍或熱栗系統熱交換器（蒸發器 )的除霜方法與配置，其包含··超過第一熱交換器（蒸發 器）、至少一壓縮機、一第二熱交換器（排熱器）和一膨 脹裝置，以線管連接以可操作的方式形成一完整的封閉回 路。 【發明背景】 在冷凍系統中若干類似空氣源熱泵或空氣冷卻器的應 用當中，當周圍溫度靠近或低於水的冷凍點時，熱吸收熱 交換器（具蒸發器功能）上將結霜。由於霜的堆積，該熱 交換器的熱交換能力和造成的系統性能將減低。因此，需 要一除霜裝置。最普通的除霜方法爲電力和熱氣除霜。第 一個方法（電力除霜）簡單，但不夠有效率，而當系統有 兩個或更多蒸發器時，則熱氣除霜方法最合適。在兩種方 式中，對一熱栗系統而言，在除霜循環期間，必須作動輔 助加熱系統以便符合加熱需要。 相關於此的美國第5·845·502號專利揭露一除霜循環 ，其中，不需要逆轉該熱泵，藉著累積器中冷媒的一加熱 裝置，該外部熱交換器的壓力和溫度被升高。雖然藉著維 持該熱泵在加熱模式使得此系統改善內部熱舒服度，但是 該除霜程序仍然需要：該加熱裝置必須足夠大才能升高吸 入壓力和使相對的飽和溫度高於水（霜）的冷凍點。基於 實用的理由，此類態式可能限制能與此種除霜方法（輻射 4 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁)562916 A7 --- ^-V. Description of the invention (π [Field of the invention] The present invention relates to a defrosting method and configuration of a heat exchanger (evaporator) of a refrigeration or heat pump system, which includes ... An exchanger (evaporator), at least one compressor, a second heat exchanger (exhauster), and an expansion device are connected in a pipe to form a complete closed circuit in an operable manner. BACKGROUND OF THE INVENTION In some applications similar to air source heat pumps or air coolers in the system, when the ambient temperature is near or below the freezing point of water, frost will form on the heat absorption heat exchanger (with evaporator function). Due to the accumulation of frost, the The heat exchange capacity of the heat exchanger and the resulting system performance will be reduced. Therefore, a defrosting device is required. The most common defrosting methods are electricity and hot gas defrosting. The first method (electric defrosting) is simple, but not enough Efficiency, and when the system has two or more evaporators, the hot gas defrost method is the most suitable. Of the two methods, for a heat pump system, the auxiliary heating system must be activated during the defrost cycle. In order to meet the heating needs, the related US Patent No. 5.845.502 discloses a defrosting cycle, in which the heat pump does not need to be reversed. By means of a heating device of the refrigerant in the accumulator, the pressure of the external heat exchanger And temperature is raised. Although the system improves internal thermal comfort by maintaining the heat pump in heating mode, the defrosting procedure still requires: the heating device must be large enough to raise the suction pressure and make the relative saturation temperature high In the freezing point of water (frost). For practical reasons, this type of formula may limit the ability to be used with this type of defrosting method (radiation 4 This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm)) (Please read the notes on the back before filling out this page)
562916 B7 五、發明說明（々） 的較佳具體實施例° 【圖式簡單說明】 參考下列圖式，將詳細說明本發明： 圖1和圖2係顯示根據表示本發明除霜操作的原理之 示意圖。 圖3和圖4顯示圖1和圖2中本發明的具體實施例之 示意圖。 圖5表示使用圖1所示之除霜方法的程序的T_S圖。 圖6表示在溫度/熵(T-S)圖表中的C〇2和R12加熱程 序之間的比較，其中，R12的除霜程序相對應於美國第 5845502號專利程序。 圖7、圖8、圖9和圖10顯示本發明的更具體實施例 的除霜循環之示意圖。 圖11表示相對於本發明專利申請範圍第4項的除霜循 環運轉實驗結果。 【元件符號說明】 A、B 子程序回路 1 壓縮機 2 第二熱交換器（排熱器、冷凝器） 3 將被除霜的（第一）熱交換（蒸發）器 6 第一膨脹裝置 6’ 第二膨脹裝置、壓力減低裝置 6 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁) 」-------- 562916 A7 B7 五、發明說明（外 ) 7 接收器/累積器 9 熱交換器 10 加熱裝置 16 、 16, 、16” 、 16”， 20、21 線管圏 2(T 迴繞圈 22 三通閥、迴繞圏 23 第一迴繞圏 (請先閱讀背面之注意事項再填寫本頁) 【本發明的詳細說明】 本發明大體上有關於冷凍與熱泵系統，更特別地但不 限制於，在過臨界程序下操作，除霜於一結霜的熱交換器 特別係具有以任何流體一特別係二氧化碳一爲冷媒的蒸發 本發明能被使用於任何較佳地具有壓力接收器/累積器 的冷凍或熱泵系統。如果需要，本發明能同時在相關於熱 泵系統的傳統除霜方法的除霜循環期間消除冷卻內部通風 裝置。此能經由一外部熱源例如電阻或廢熱（例如從汽車 冷卻系統）或任何其它適當的能配合接收器/累積器之中或 沿著回路中的冷媒通路的連接管路的裝置來達成。熱同時 能從一儲存單位中被供應。本發明能與具有接收器/累積器 的次臨界和過臨界冷凍和熱泵兩者系統一起使用。本發明 同時能與僅具有一蒸發器的冷凍和熱泵系統一起使用。 根據本發明的除霜循環操作方法參考可能是熱泵系統 7 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） 562916 A7 ^_____B7____ 五、發明說明（〇 或冷凍（冷卻）系統的圖1和圖2來說明。該系統包含一 壓縮機1、一將被除霜的熱交換器3、一熱交換器9、兩個 膨脹裝置··第一 6和第二6,，一第二熱交換器2 (排熱器 )、閥門16’和16”’、一接收器/累積器7和一加熱裝置1〇 。該第二膨脹裝置6’係被設在一相對於配置於熱交換器（ 蒸發器）3之後的閥門16”，的旁通線管圈中。由一加熱裝 置的熱量增加和迴繞閥門16”，的第二膨脹裝置6,和迴繞第 一膨脹裝置6的閥門16’等的提供代表本發明的主要創新 特色，並且藉著保持基本上與壓縮機（1)的洩放壓力相同的 壓力使得該熱交換器3能接受除霜，因此，當高壓洩放壓 力氣體從壓縮機1流過放熱該所述熱交換器3的熱交換器 時，該熱交換器3被除霜。該加熱裝置10將熱較佳地經由 一接收器/累積器7加到冷媒上，但是在除霜循環期間能同 時交替地或額外地沿著冷媒通道將熱加到系統的任何地方 中的冷媒處。 正常操作（圖1): 在正常操作下，被提供在一相對於閥門16”’的旁通圏 中的該第二膨脹裝置6’和被提供在一相對於第一膨脹裝置 6的旁通圈中的閥門16”係關閉的，同時另一方面閥門16”’ 係打開的。其同時應該瞭解到：該第二膨脹裝置6’能爲一 毛細管或類似裝置，技術上而言，其並非”封閉的”，但在 實際上在正常操作期間並沒有冷媒流動。該循環冷媒在外 部熱交換器3之中蒸發。該冷媒在通過內熱交換器9並在 8 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐〉 (請先閱讀背面之注意事項再填寫本頁) 約---------·. 562916 A7 __B7___ 五、發明說明（b ) 該處超加熱之前先進入接收器/累加器7。該超加熱蒸氣由 壓縮機1吸入。在其進入第二熱交換器（排熱器）2之前 ，該蒸氣的壓力和溫度於是被壓縮機1所增加。端視該壓 力的大小，該冷媒蒸氣藉由排熱不是被冷凝（在次臨界壓 力）就是被冷卻（在超臨界壓力）。在其壓力被膨脹裝置 6降低至蒸發壓力之前，該高壓冷媒於是通過內熱交換器9 ，完成該循環。 除霜循環： 請參考圖1，在除霜開始之初，閥門16’將打開而閥門 16”’將關閉。根據本發明，該第二熱交換器（排熱器）2和 第一熱交換器（蒸發器）3將以串聯或倂聯來耦合，並如 上所述地，經歷與壓縮機洩放壓力幾乎相同的壓力。如果 需要，該熱交換器2同時能被迴繞。此可爲冷凍系統中的 例子，其中，在除霜循環期間，並不需要藉由所述的熱交 換器來排熱（圖2)。 在其進入該熱交換器2之前，該冷媒蒸氣的壓力與溫 度被壓縮機1所升高。如果是在除霜循環期間需要熱傳遞 的熱泵操作，則該（冷媒壓力）藉由散熱給熱庫（如果是 空氣系統，其爲內部空氣）來被冷卻。在其經由閥門16’ 進入將被除霜的熱交換器（蒸發器）3之前，該高壓冷媒 能通過內熱交換器9或能被交替地迴繞（如圖！所示）。 在熱交換器3出口的冷卻冷媒於是通過膨脹閥6’，靠著該 膨脹閥6’其壓力被下降至接收器/累積器7中的壓力。熱較 9 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） (請先閱讀背面之注意事項再填寫本頁)562916 B7 V. Preferred embodiment of the invention description (々) [Simplified description of the drawings] The invention will be described in detail with reference to the following drawings: Figures 1 and 2 show the principle of defrost operation according to the present invention. schematic diagram. 3 and 4 are schematic diagrams of a specific embodiment of the present invention in Figs. FIG. 5 shows a T_S diagram of a program using the defrosting method shown in FIG. 1. Figure 6 shows a comparison between the CO2 and R12 heating procedures in a temperature / entropy (T-S) chart, where the defrost procedure of R12 corresponds to the US patent No. 5845502. Figures 7, 8, 9 and 10 show schematic diagrams of a defrost cycle in a more specific embodiment of the present invention. Fig. 11 shows the results of the defrosting cycle operation test with respect to item 4 of the scope of patent application of the present invention. [Description of component symbols] A, B subroutine circuit 1 compressor 2 second heat exchanger (exhauster, condenser) 3 (first) heat exchange (evaporator) to be defrosted 6 first expansion device 6 '' Second expansion device, pressure reduction device 6 This paper size is applicable to China National Standard (CNS) A4 specification (210 X 297 mm) (Please read the precautions on the back before filling this page) '' ------- -562916 A7 B7 V. Description of the invention (outside) 7 Receiver / accumulator 9 Heat exchanger 10 Heating device 16, 16, 16, 16 ", 16", 20, 21 Wire tube 圏 2 (T return ring 22 3-way valve 、 Rewind 第一 23 First rewind 圏 (Please read the notes on the back before filling this page) [Detailed description of the present invention] The present invention is generally related to refrigeration and heat pump systems, more specifically but not limited to, in the critical Operate under the program, the defrost on a frosted heat exchanger especially has the evaporation of any fluid, especially carbon dioxide, as a refrigerant. The present invention can be used in any refrigeration or heat pump that preferably has a pressure receiver / accumulator System. If needed, this The invention can simultaneously eliminate cooling of internal ventilation during a defrost cycle of a conventional defrost method associated with a heat pump system. This can be via an external heat source such as a resistor or waste heat (such as from a car cooling system) or any other suitable receiver capable of cooperating This is achieved by devices in the / accumulator or along the connecting pipes of the refrigerant path in the circuit. Heat can be supplied simultaneously from a storage unit. The invention can be used with subcritical and supercritical freezing with receiver / accumulator It can be used with both heat pump systems. The invention can be used with both refrigeration and heat pump systems with only one evaporator. The defrost cycle operation method according to the invention may refer to the heat pump system. 7 This paper size applies to Chinese national standards (CNS ) A4 size (210 X 297 mm) 562916 A7 ^ _____ B7____ 5. Description of the invention (0 or Figure 1 and Figure 2 of the refrigeration (cooling) system. The system contains a compressor 1, a heat to be defrosted, Exchanger 3, a heat exchanger 9, two expansion devices ... first 6 and second 6, a second heat exchanger 2 (exhauster), valves 16 'and 16 " A receiver / accumulator 7 and a heating device 10. The second expansion device 6 'is provided in a bypass line with respect to the valve 16 "disposed behind the heat exchanger (evaporator) 3. In the circle. The addition of heat from a heating device and rewinding of the valve 16 ", the second expansion device 6, and the valve 16 'of the first expansion device 6 and the like represent the main innovative features of the present invention, and by maintaining the basic The same pressure as the discharge pressure of the compressor (1) makes the heat exchanger 3 capable of receiving defrosting. Therefore, when high pressure relief pressure gas flows from the compressor 1, the heat exchange of the heat exchanger 3 is released. The heat exchanger 3 is defrosted. The heating device 10 preferably adds heat to the refrigerant via a receiver / accumulator 7 but can simultaneously or alternately or additionally add heat to the refrigerant in any part of the system during the defrosting cycle Office. Normal operation (Fig. 1): In normal operation, the second expansion device 6 'is provided in a bypass ring relative to the valve 16 "' and the bypass device is provided in a bypass relative to the first expansion device 6. The valve 16 "in the circle is closed, and at the same time the valve 16" 'is open. It should also be understood that the second expansion device 6' can be a capillary tube or similar device. Technically, it is not "Closed", but in practice, no refrigerant flows during normal operation. The circulating refrigerant evaporates in the external heat exchanger 3. The refrigerant passes through the internal heat exchanger 9 and applies the Chinese national standard at 8 paper sizes ( CNS) A4 specification (210 X 297 mm) (Please read the precautions on the back before filling out this page) About ---------. 562916 A7 __B7___ V. Description of the invention (b) Super heating at this place It previously entered the receiver / totalizer 7. The superheated vapor is sucked in by the compressor 1. Before it enters the second heat exchanger (exhauster) 2, the pressure and temperature of the vapor are then increased by the compressor 1. Depending on the magnitude of the pressure, the refrigerant vapor is The heat is either condensed (at subcritical pressure) or cooled (at supercritical pressure). Before its pressure is reduced to the evaporation pressure by the expansion device 6, the high-pressure refrigerant then passes through the internal heat exchanger 9 to complete the cycle. Defrost cycle : Please refer to Figure 1. At the beginning of the defrost, the valve 16 'will be opened and the valve 16 "' will be closed. According to the present invention, the second heat exchanger (exhauster) 2 and the first heat exchanger (evaporation The compressor 3 will be coupled in series or in series, and as described above, will experience almost the same pressure as the compressor discharge pressure. If necessary, the heat exchanger 2 can be rewinded at the same time. This can be used in refrigeration systems Example, in which, during the defrost cycle, it is not necessary to dissipate heat through the heat exchanger (Figure 2). Before it enters the heat exchanger 2, the pressure and temperature of the refrigerant vapor are compressed by the compressor 1 If it is a heat pump operation that requires heat transfer during the defrost cycle, the (refrigerant pressure) is cooled by dissipating heat to the heat store (if it is an air system, it is the internal air). It passes through valve 16 'Enter Before the heat exchanger (evaporator) 3 to be defrosted, the high-pressure refrigerant can pass through the inner heat exchanger 9 or can be alternately wound (as shown in the picture!). The cooling refrigerant at the outlet of the heat exchanger 3 then passes through expansion. The valve 6 ', against which the pressure of the expansion valve 6' is lowered to the pressure in the receiver / accumulator 7. The heat is larger than 9 This paper size applies the Chinese National Standard (CNS) A4 specification (210 X 297 mm) (please (Read the notes on the back before filling out this page)
562916 A7 _ B7__ 五、發明說明（） 佳地被加到該接收器/累積器7中的冷媒’以將進入該接收 器/累積器7中的流體冷媒蒸發。 應用的型態和其要求決定加熱裝置的型態和需要的熱 量以便實施該除霜程序。例如，使用具吸入氣體冷卻馬達 的壓縮機，由馬達所散發的熱和/或壓縮機的熱能被當作” 熱源”來使用，以便在除霜循環期間以最小的能源輸入量， 將熱加給該冷媒。圖Π表示若干使用吸入氣體所冷卻的 壓縮機的實驗結果，其中，壓縮熱和由壓縮機馬達所散發 的熱量被當作”熱源”來使用。或者在一水加熱器熱泵系統 的例子當中，在排熱器和/或熱水儲存桶的水所累積的熱能 被當作”熱源”來使用。 使用超臨界熱排放壓力，其存在一額外增加此發明的 更具彈性的”自由度”。雖然在次臨界系統中在冷凝器、熱 交換器2中的壓力（和飽和溫度）藉著在所述熱交換器（ 排熱器）中的熱交換程序的平衡被自動決定，該超臨界壓 力能被主動地控制以最佳化該程序與熱交換性能。 圖3表示本發明進一步的具體實施例，其中，熱交換 器2和3使用一三通閥22以倂聯來親合，其中，端視所需 要的除霜速度和加熱效果，部分來自壓縮機的冷媒經由一 迴繞圈20被引導至該熱交換器3處。在此範例中，從熱 交換器2引導出的冷媒藉著在第二迴繞圈的閥門16”的打 開而迴繞過該熱交換器3。 進一步地，圖4表示另外一個具體實施例，其中，使 用一三通閥22將該熱交換器2 (排熱器）部分地或整個地 10 ______________ - -— —— - 木紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐） ---------------------訂---------線 (請先閱讀背面之注意事項再填寫本頁) 562916 A7 __B7____ 五、發明說明（？） 迴繞過另一個線管圈21。此具體實施例在需要快速除霜的 狀況係很有用的。 根據本發明，該超臨界壓力能被主動地控制以增加在 壓縮機1之後在如圖5所示的除霜循環期間的冷媒溫度和 比焓。在壓縮機1 (圖表中的點b)之後的該較高冷媒比焓 係該洩放壓力增加時增加壓縮功所造成的結果。在此方面 ，增加壓縮功的可能性能被視爲該除霜方法的”保留加熱裝 置”。如在一例子，在一熱泵系統中，在具高加熱需求的除 霜循環期間，本發明的此特色對符合內部熱舒服要求係有 用的。將該第二熱交換器（冷凝器）2和將被除霜的第一 熱交換器（蒸發器）3在除霜循環期間以倂聯而非串聯來 運作以實施除霜係可能的。 本發明所增加的除霜效果（由於增加功的比焓）與例 如美國第5.845.502號專利所表示的結果之間的比較進一 步地表示在圖7之中。右手邊的圖表代表本發明的程序， 而左手邊的圖表代表美國專利的程序。可淸楚地看到，本 發明的除霜溫度比較高。 在熱泵或熱回收系統的其它應用當中，其主要目的在 於盡可能迅速且有效地完成該除霜循環。在這些例子當中 ’該熱交換器（排熱器）2，在除霜循環期間能如圖2所示 的被迴繞，其中具有閥門16的迴繞線管圈被提供，閥門 16在此類例子中係打開的。該除霜循環因此可比在以往的 例子中更快的被執行。且該內部熱交換器9可藉由具有閥 門16’的迴繞線管圈被迴繞，如同在圖1中所示。 11 本紙張尺度適用中國國家標準（CNS)A4規格（21〇 x 297公釐） (請先閱讀背面之注意事項再填寫本頁) --------訂---------· 562916 B7 五、發明說明（巧） 在所附的申請專利範圍中所界定的本發明係不受限於 上述的實施例。因此根據本發明，該除霜循環可與任何具 有一接收器/蓄積器的冷凍以及熱泵系統一起使用。此表 示在圖7-9之中，在不同的具體實施例中同樣的除霜循環 被執行，其中，例如流動逆轉裝置4和5各別地被提供在 子程序回路A和B之中以便迅速地從熱泵改變到冷卻操作 模式。圖10表示根據本發明的基本除霜原理，其中，一中 級壓力接收器被使用。該所述圖式表示一用於系統的除霜 循環，在該系統中，不需要藉該熱交換器2在除霜循環期 間排熱，而是使用壓縮熱當作加熱裝置。在除霜循環期間 ，閥門16’和16”將被打開而閥門16”’將被關閉。結果，在 其進入將被除霜的該熱交換器3之前，從壓縮機出來的高 壓高溫氣體中通過閥門16’。該被冷卻的冷媒的壓力於是 藉著膨脹閥6”’被減低至中級壓力接收器7中的壓力。因爲 該所述接收器現在係經由提供閥門16”’的迴繞圈直接與壓 縮機的吸入端相聯繫，所以該所述接收器中的壓力將基本 上與壓縮機吸入壓力相同。當吸入氣體被壓縮機壓縮至較 高的壓力與溫度時，壓縮熱被加到冷媒中。因爲，在系統 中沒有外加熱裝置，該壓縮機的吸入壓力和壓力接收器7 的吸入壓力將減少直到其發現一平衡壓力爲止。 12 本紙張尺度適用中國國家標準（CNS)A4規格（210 X 297公釐〉 (請先閱讀背面之注意事項再填寫本頁) tr---------.562916 A7 _ B7__ V. Description of the invention () Refrigerant which is preferably added to the receiver / accumulator 7 'to evaporate the fluid refrigerant entering the receiver / accumulator 7. The type of application and its requirements determine the type of heating device and the amount of heat required in order to implement the defrosting procedure. For example, using a compressor with a suction gas-cooled motor, the heat dissipated by the motor and / or the compressor's thermal energy is used as a "heat source" to add heat to the energy source during the defrost cycle with minimal energy input. The refrigerant. Figure Π shows the experimental results of several compressors cooled with suction gas, in which the heat of compression and the heat dissipated by the compressor motor are used as "heat sources". Or in the case of a water heater heat pump system, the heat energy accumulated in the water of the heat rejector and / or hot water storage tank can be used as a "heat source". With supercritical heat discharge pressure, there is a more flexible "degree of freedom" which adds to this invention. Although the pressure (and saturation temperature) in the condenser, heat exchanger 2 in the subcritical system is automatically determined by the balance of the heat exchange program in the heat exchanger (exhauster), the supercritical pressure Can be actively controlled to optimize the program and heat exchange performance. FIG. 3 shows a further specific embodiment of the present invention, in which the heat exchangers 2 and 3 are coupled with a three-way valve 22 in a coupling manner, wherein the required defrosting speed and heating effect are partially derived from the compressor The refrigerant is guided to the heat exchanger 3 through a loop 20. In this example, the refrigerant guided from the heat exchanger 2 bypasses the heat exchanger 3 by opening the valve 16 "in the second winding circle. Further, FIG. 4 shows another specific embodiment, in which, Use a three-way valve 22 to partially or completely heat exchanger 2 (exhaust heat exchanger) 10 ______________------The size of wood paper is applicable to China National Standard (CNS) A4 (210 X 297 mm)- -------------------- Order --------- line (please read the notes on the back before filling this page) 562916 A7 __B7____ V. Invention Explanation (?) Bypassing another coil ring 21. This specific embodiment is useful in situations where rapid defrosting is required. According to the present invention, the supercritical pressure can be actively controlled to increase Refrigerant temperature and specific enthalpy during the defrost cycle as shown in Figure 5. The higher specific refrigerant enthalpy after compressor 1 (point b in the graph) is a result of increasing the compression work as the relief pressure increases. In this respect, the possible performance of increasing the compression work is regarded as the "retention heating device" of the defrosting method. In one example, in a heat pump system, this feature of the present invention is useful for meeting internal thermal comfort requirements during a defrosting cycle with high heating requirements. The second heat exchanger (condenser) 2 and the The defrosted first heat exchanger (evaporator) 3 is possible to operate in decoupling rather than in series during the defrost cycle to implement the defrost system. The increased defrost effect of the present invention (due to the increased specific enthalpy of work) ) And, for example, the results represented by U.S. Patent No. 5.845.502 are further shown in Figure 7. The chart on the right hand side represents the program of the present invention and the chart on the left hand side represents the program of the U.S. patent. It is clear that the defrost temperature of the present invention is relatively high. In other applications of heat pumps or heat recovery systems, the main purpose is to complete the defrost cycle as quickly and efficiently as possible. In these examples, the heat exchanger (Exhaust Heater) 2. It can be rewinded during the defrosting cycle as shown in FIG. 2, in which a winding coil with a valve 16 is provided, and the valve 16 is opened in such an example. The defrost cycle is caused by It can be executed faster than in the previous examples. And the internal heat exchanger 9 can be rewinded by a winding coil with a valve 16 ', as shown in Figure 1. 11 This paper size applies Chinese national standards (CNS) A4 specification (21〇x 297 mm) (Please read the precautions on the back before filling this page) -------- Order --------- · 562916 B7 V. Invention Note (Clever) The invention as defined in the scope of the attached patent application is not limited to the embodiments described above. Therefore, according to the invention, the defrost cycle can be used with any refrigeration and heat pump with a receiver / accumulator System together. This is shown in Figs. 7-9. The same defrosting cycle is performed in different embodiments. For example, the flow reversing devices 4 and 5 are separately provided in the subroutine circuits A and B to quickly Ground is changed from heat pump to cooling operation mode. Figure 10 shows the basic defrosting principle according to the invention, in which a medium pressure receiver is used. The said diagram shows a defrosting cycle for a system in which the heat is not required to be exhausted during the defrosting cycle by the heat exchanger 2 but the heat of compression is used as a heating device. During the defrost cycle, valves 16 'and 16 "will be opened and valve 16"' will be closed. As a result, the high-pressure high-temperature gas from the compressor passes through the valve 16 'before it enters the heat exchanger 3 to be defrosted. The pressure of the cooled refrigerant is then reduced to the pressure in the intermediate pressure receiver 7 by means of the expansion valve 6 "'. Because the receiver is now directly connected to the suction of the compressor via a winding loop providing the valve 16"' End-to-end, so the pressure in the receiver will be essentially the same as the compressor suction pressure. When the suction gas is compressed by the compressor to a higher pressure and temperature, the compression heat is added to the refrigerant. Because there is no external heating device in the system, the suction pressure of the compressor and the suction pressure of the pressure receiver 7 will decrease until it finds an equilibrium pressure. 12 This paper size applies to China National Standard (CNS) A4 (210 X 297 mm) (Please read the precautions on the back before filling this page) tr ---------.