TWI630359B - Compressor apparatus - Google Patents
Compressor apparatus Download PDFInfo
- Publication number
- TWI630359B TWI630359B TW105111428A TW105111428A TWI630359B TW I630359 B TWI630359 B TW I630359B TW 105111428 A TW105111428 A TW 105111428A TW 105111428 A TW105111428 A TW 105111428A TW I630359 B TWI630359 B TW I630359B
- Authority
- TW
- Taiwan
- Prior art keywords
- compression unit
- compression
- unit
- fluid
- rotation
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
- F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
一種壓縮設備，包括一第一壓縮單元及一第二壓縮單元。第一壓縮單元適於壓縮一流體。第二壓縮單元連接於第一壓縮單元。在第一壓縮單元壓縮流體之後，第二壓縮單元適於壓縮流體。第二壓縮單元的容積效率大於第一壓縮單元的容積效率。A compression device includes a first compression unit and a second compression unit. The first compression unit is adapted to compress a fluid. The second compression unit is coupled to the first compression unit. After the first compression unit compresses the fluid, the second compression unit is adapted to compress the fluid. The volumetric efficiency of the second compression unit is greater than the volumetric efficiency of the first compression unit.
Description
本發明是有關於一種壓縮設備，且特別是有關於一種單機雙級壓縮設備。This invention relates to a compression device and, more particularly, to a stand-alone two-stage compression device.
壓縮機是一種將氣體壓縮並提升氣體壓力的裝置，其應用廣泛，常見的應用領域包括暖通空調、冷凍循環、提供工業驅動動力、矽化工、石油化工、天然氣輸送等。依據運作原理，壓縮機可分為容積式(positive-displacement)壓縮機及氣體動力式(aerodynamic)壓縮機。The compressor is a device that compresses the gas and raises the pressure of the gas. It is widely used. Common applications include HVAC, refrigeration cycle, industrial drive power, chemical industry, petrochemical, natural gas transportation. According to the operating principle, the compressor can be divided into a positive-displacement compressor and an aerodynamic compressor.
以容積式壓縮機而言，其將氣體導入密閉空間中，透過壓縮空間體積而使氣體壓力上升。依據壓縮方式的不同，容積式壓縮機可分為往復式、迴轉式、渦卷式、螺桿式等種類。目前的單機雙級壓縮機大多以相同種類的兩壓縮機所構成，如雙往復式壓縮機或雙螺桿式壓縮機。然而，同一種類的壓縮機其性質相同，難以結合不同種類壓縮機的優點來有效提升壓縮效能。In the case of a positive displacement compressor, the gas is introduced into the sealed space, and the gas pressure is increased by the volume of the compressed space. Depending on the compression method, the volumetric compressor can be classified into reciprocating type, rotary type, scroll type, and screw type. Most of the current single-stage two-stage compressors are composed of two compressors of the same kind, such as a double reciprocating compressor or a twin-screw compressor. However, the same type of compressor has the same properties, and it is difficult to combine the advantages of different types of compressors to effectively improve the compression efficiency.
本發明提供一種壓縮設備，結合不同種類壓縮機的優點來提升壓縮效能。The present invention provides a compression apparatus that combines the advantages of different types of compressors to increase compression performance.
本發明的壓縮設備包括一第一壓縮單元及一第二壓縮單元。第一壓縮單元適於壓縮一流體。第二壓縮單元連接於第一壓縮單元。在第一壓縮單元壓縮流體之後，第二壓縮單元適於壓縮流體。第二壓縮單元的容積效率大於第一壓縮單元的容積效率。The compression device of the present invention includes a first compression unit and a second compression unit. The first compression unit is adapted to compress a fluid. The second compression unit is coupled to the first compression unit. After the first compression unit compresses the fluid, the second compression unit is adapted to compress the fluid. The volumetric efficiency of the second compression unit is greater than the volumetric efficiency of the first compression unit.
在本發明的一實施例中，上述的第一壓縮單元是螺桿式壓縮單元，第二壓縮單元是渦卷式壓縮單元。In an embodiment of the invention, the first compression unit is a screw compression unit and the second compression unit is a scroll compression unit.
本發明的壓縮設備包括一第一壓縮單元及一第二壓縮單元。第一壓縮單元適於壓縮一流體。第二壓縮單元連接於第一壓縮單元。在第一壓縮單元壓縮流體之後，第二壓縮單元適於壓縮流體。第一壓縮單元是螺桿式壓縮單元，第二壓縮單元是渦卷式壓縮單元。The compression device of the present invention includes a first compression unit and a second compression unit. The first compression unit is adapted to compress a fluid. The second compression unit is coupled to the first compression unit. After the first compression unit compresses the fluid, the second compression unit is adapted to compress the fluid. The first compression unit is a screw compression unit and the second compression unit is a scroll compression unit.
在本發明的一實施例中，上述的第二壓縮單元的容積效率大於第一壓縮單元的容積效率。In an embodiment of the invention, the volumetric efficiency of the second compression unit is greater than the volumetric efficiency of the first compression unit.
在本發明的一實施例中，上述的第一壓縮單元的排氣量大於第二壓縮單元的排氣量。In an embodiment of the invention, the amount of exhaust of the first compression unit is greater than the amount of exhaust of the second compression unit.
在本發明的一實施例中，上述的壓縮設備具有一入口端及一出口端，其中第一壓縮單元位於入口端與第二壓縮單元之間，第二壓縮單元位於第一壓縮單元與出口端之間，流體適於透過入口端進入第一壓縮單元，且適於透過出口端離開第二壓縮單元。In an embodiment of the invention, the compression device has an inlet end and an outlet end, wherein the first compression unit is located between the inlet end and the second compression unit, and the second compression unit is located at the first compression unit and the outlet end. Between the two, the fluid is adapted to enter the first compression unit through the inlet end and is adapted to exit the second compression unit through the outlet end.
在本發明的一實施例中，上述的第一壓縮單元適於壓縮流體而使流體具有一第一壓力，第二壓縮單元適於壓縮具有第一壓力的流體而使流體具有一第二壓力，第二壓力大於第一壓力。In an embodiment of the invention, the first compression unit is adapted to compress a fluid such that the fluid has a first pressure, and the second compression unit is adapted to compress the fluid having the first pressure to cause the fluid to have a second pressure, The second pressure is greater than the first pressure.
在本發明的一實施例中，上述的壓縮設備包括一驅動單元，其中驅動單元適於同時驅動第一壓縮單元及第二壓縮單元。In an embodiment of the invention, the compression device comprises a driving unit, wherein the driving unit is adapted to drive the first compression unit and the second compression unit simultaneously.
在本發明的一實施例中，上述的第一壓縮單元連接於驅動單元與第二壓縮單元之間。In an embodiment of the invention, the first compression unit is connected between the driving unit and the second compression unit.
在本發明的一實施例中，上述的驅動單元連接於第一壓縮單元與第二壓縮單元之間。In an embodiment of the invention, the driving unit is connected between the first compression unit and the second compression unit.
在本發明的一實施例中，上述的第一壓縮單元適於沿一第一轉動軸線作動，第二壓縮單元適於沿一第二轉動軸線作動，第一轉動軸線與第二轉動軸線共軸。In an embodiment of the invention, the first compression unit is adapted to be actuated along a first axis of rotation, the second compression unit is adapted to act along a second axis of rotation, the first axis of rotation being coaxial with the second axis of rotation .
在本發明的一實施例中，上述的壓縮設備包括一聯軸器，其中第一壓縮單元具有一第一轉軸，第二壓縮單元具有一第二轉軸，第一轉軸與第二轉軸藉由聯軸器而相連接。In an embodiment of the invention, the compression apparatus includes a coupling, wherein the first compression unit has a first rotation shaft, and the second compression unit has a second rotation shaft, and the first rotation shaft and the second rotation shaft are coupled by The shafts are connected together.
在本發明的一實施例中，上述的第一壓縮單元具有一第一轉軸，第二壓縮單元具有一第二轉軸，第一轉軸與第二轉軸為同一轉軸。In an embodiment of the invention, the first compression unit has a first rotating shaft, and the second compression unit has a second rotating shaft, and the first rotating shaft and the second rotating shaft are the same rotating shaft.
基於上述，本發明將不同種類的壓縮單元整合於單一壓縮設備，以結合不同種類壓縮機的優點。具體而言，第一壓縮單元可為結構強度較高的螺桿式壓縮單元，而第二壓縮單元可為較不易內漏而容積效率較高的渦卷式壓縮單元。當利用第一壓縮單元進行第一階段壓縮時，若進入第一壓縮單元的部分流體(如冷媒)非預期地為液態並在第一壓縮單元內氣化而瞬間膨脹，則第一壓縮單元可藉其高結構強度而避免因流體瞬間膨脹而遭受破壞。此外，當利用第二壓縮單元進行第二階段壓縮時，進入第二壓縮單元的流體因已進行過第一階段壓縮而具有較大壓力，第二壓縮單元可藉其不易內漏的特性而避免流體因壓力較大而產生內漏。藉此，可使壓縮設備具有良好的壓縮效能，並提升壓縮設備的耐用性。Based on the above, the present invention integrates different types of compression units into a single compression device to combine the advantages of different types of compressors. Specifically, the first compression unit may be a screw compression unit having a higher structural strength, and the second compression unit may be a scroll compression unit that is less susceptible to internal leakage and has higher volumetric efficiency. When the first stage compression is performed by the first compression unit, if a part of the fluid (such as a refrigerant) entering the first compression unit is undesirably liquid and instantaneously expanded by gasification in the first compression unit, the first compression unit may By virtue of its high structural strength, it is prevented from being damaged by the instantaneous expansion of the fluid. In addition, when the second compression unit performs the second-stage compression, the fluid entering the second compression unit has a large pressure due to the first-stage compression, and the second compression unit can be avoided by the characteristic of not easily leaking. The fluid creates an internal leak due to the high pressure. Thereby, the compression device can have good compression performance and improve the durability of the compression device.
為讓本發明的上述特徵和優點能更明顯易懂，下文特舉實施例，並配合所附圖式作詳細說明如下。The above described features and advantages of the invention will be apparent from the following description.
圖1是本發明一實施例的壓縮設備的示意圖。請參考圖1，本實施例的壓縮設備100包括一第一壓縮單元110、一第二壓縮單元120及一驅動單元130。第二壓縮單元120連接於第一壓縮單元110，驅動單元130例如是馬達且適於同時驅動第一壓縮單元110及第二壓縮單元120作動。本實施例的壓縮設備100例如是應用於冷凍空調系統或其他領域，本發明不對此加以限制。1 is a schematic diagram of a compression device in accordance with an embodiment of the present invention. Referring to FIG. 1 , the compression device 100 of the present embodiment includes a first compression unit 110 , a second compression unit 120 , and a driving unit 130 . The second compression unit 120 is coupled to the first compression unit 110. The driving unit 130 is, for example, a motor and is adapted to simultaneously drive the first compression unit 110 and the second compression unit 120 to operate. The compression apparatus 100 of the present embodiment is applied to, for example, a refrigerating air conditioning system or other fields, and the present invention is not limited thereto.
第一壓縮單元110適於壓縮一流體(例如是冷媒)而使所述流體具有第一壓力。在第一壓縮單元110壓縮所述流體之後，所述流體從第一壓縮單元110流至第二壓縮單元120，且第二壓縮單元120適於進一步壓縮所述流體而使所述流體具有大於第一壓力的第二壓力。亦即，本實施例的壓縮設備100是包含了第一壓縮單元110及第二壓縮單元120的單機雙級壓縮機，第一壓縮單元110及第二壓縮單元120依序對流體進行第一階段壓縮及第二階段壓縮。The first compression unit 110 is adapted to compress a fluid (e.g., a refrigerant) to cause the fluid to have a first pressure. After the first compression unit 110 compresses the fluid, the fluid flows from the first compression unit 110 to the second compression unit 120, and the second compression unit 120 is adapted to further compress the fluid such that the fluid has a greater than The second pressure of a pressure. That is, the compression device 100 of the present embodiment is a single-stage two-stage compressor including the first compression unit 110 and the second compression unit 120, and the first compression unit 110 and the second compression unit 120 sequentially perform the first stage of the fluid. Compression and second stage compression.
在本實施例中，第一壓縮單元110例如是螺桿式壓縮單元，第二壓縮單元120例如是渦卷式壓縮單元。從而，第二壓縮單元120的容積效率大於第一壓縮單元110的容積效率，第一壓縮單元110的排氣量大於第二壓縮單元120的排氣量，且第一壓縮單元110的結構強度大於第二壓縮單元120的結構強度。在其他實施例中，第一壓縮單元110與第二壓縮單元120可分別為其他種類的壓縮單元，本發明不對此加以限制。In the present embodiment, the first compression unit 110 is, for example, a screw compression unit, and the second compression unit 120 is, for example, a scroll compression unit. Thus, the volumetric efficiency of the second compression unit 120 is greater than the volumetric efficiency of the first compression unit 110, the displacement of the first compression unit 110 is greater than the displacement of the second compression unit 120, and the structural strength of the first compression unit 110 is greater than The structural strength of the second compression unit 120. In other embodiments, the first compression unit 110 and the second compression unit 120 are respectively other types of compression units, which are not limited by the present invention.
在本實施例的上述配置方式之下，壓縮設備100可發揮第一壓縮單元110(螺桿式壓縮單元)所具有的高結構強度、耐液壓縮、可容調、排氣量大等優點，亦可發揮第二壓縮單元120(渦卷式壓縮單元)所具有的不易內漏、容積效率大等優點。舉例來說，當利用第一壓縮單元110進行第一階段壓縮時，若進入第一壓縮單元110的部分流體(如冷媒)非預期地為液態並在第一壓縮單元110內氣化而瞬間膨脹，則第一壓縮單元110可藉其高結構強度而避免因流體瞬間膨脹而遭受破壞。此外，當利用第二壓縮單元120進行第二階段壓縮時，進入第二壓縮單元120的流體因已進行過第一階段壓縮而具有較大壓力，第二壓縮單元120可藉其不易內漏的特性而避免流體因壓力較大而產生內漏。藉此，可使壓縮設備100具有良好的壓縮效能，並提升壓縮設備100的耐用性。Under the above configuration mode of the embodiment, the compression device 100 can exert the advantages of high structural strength, liquid compression resistance, tolerance, and large exhaust volume of the first compression unit 110 (screw compression unit). The second compression unit 120 (volute compression unit) can exhibit the advantages of not easily leaking, and having high volumetric efficiency. For example, when the first compression unit 110 performs the first-stage compression, if a part of the fluid (such as the refrigerant) entering the first compression unit 110 is undesirably liquid and vaporized in the first compression unit 110, it expands instantaneously. The first compression unit 110 can avoid damage due to instantaneous expansion of the fluid by its high structural strength. In addition, when the second compression unit 120 performs the second-stage compression, the fluid entering the second compression unit 120 has a large pressure due to the first-stage compression, and the second compression unit 120 can be easily leak-tight. Characteristics to avoid fluid leakage due to high pressure. Thereby, the compression device 100 can be made to have good compression performance and improve the durability of the compression device 100.
圖2是圖1的壓縮設備與習知雙級壓縮機的耗電量的比較圖。圖3是圖1的壓縮設備與習知雙級壓縮機的性能係數(COP)的比較圖。圖2及圖3中的曲線A對應於本實施例的壓縮設備100，曲線B對應於習知雙往復式壓縮單元的雙級壓縮機，曲線C對應於習知雙螺桿式壓縮單元的雙級壓縮機。如圖2及圖3所示，在蒸發溫度-25℃至-60℃，本實施例的壓縮設備100的耗電量明顯低於習知兩種雙級壓縮機的耗電量，且本實施例的壓縮設備100的性能係數明顯高於習知雙級壓縮機的性能係數。所述性能係數定義為冷房能力(kW)與耗電量(kW)的比值。2 is a graph comparing the power consumption of the compression apparatus of FIG. 1 with a conventional two-stage compressor. 3 is a graph comparing the coefficient of performance (COP) of the compression apparatus of FIG. 1 with a conventional two-stage compressor. The curve A in FIG. 2 and FIG. 3 corresponds to the compression device 100 of the present embodiment, the curve B corresponds to the two-stage compressor of the conventional double reciprocating compression unit, and the curve C corresponds to the two-stage compression of the conventional twin-screw compression unit. compressor. As shown in FIG. 2 and FIG. 3, the power consumption of the compression apparatus 100 of the present embodiment is significantly lower than that of the conventional two-stage compressors at an evaporation temperature of -25 ° C to -60 ° C. The coefficient of performance of the compression device 100 is significantly higher than that of the conventional two-stage compressor. The coefficient of performance is defined as the ratio of cold room capacity (kW) to power consumption (kW).
以下進一步說明本實施例的壓縮設備100的具體配置方式。在本實施中，壓縮設備100具有一入口端E1及一出口端E2，第一壓縮單元110位於入口端E1與第二壓縮單元120之間，第二壓縮單元120位於第一壓縮單元110與出口端E2之間。所述流體適於透過入口端E1進入第一壓縮單元110，且適於透過出口端E2離開第二壓縮單元120。需說明的是，圖1所示第一壓縮單元110、第二壓縮單元120及驅動單元130之結構形狀僅為示意，並非用以限制本發明。此外，所述流體例如是藉由依序通過入口端E1、第一壓縮單元110、第二壓縮單元120及出口端E2之流路而傳遞，此流路之具體結構可依壓縮設備100實際上的結構設計而配置，於此不加以贅述。The specific configuration of the compression device 100 of the present embodiment is further described below. In the present embodiment, the compression device 100 has an inlet end E1 and an outlet end E2. The first compression unit 110 is located between the inlet end E1 and the second compression unit 120. The second compression unit 120 is located at the first compression unit 110 and the outlet. Between the ends E2. The fluid is adapted to enter the first compression unit 110 through the inlet end E1 and is adapted to exit the second compression unit 120 through the outlet end E2. It should be noted that the structural shapes of the first compression unit 110, the second compression unit 120, and the driving unit 130 shown in FIG. 1 are only schematic and are not intended to limit the present invention. In addition, the fluid is transferred by, for example, a flow path through the inlet end E1, the first compression unit 110, the second compression unit 120, and the outlet end E2. The specific structure of the flow path may be actual according to the compression device 100. The structure is designed and configured, and will not be described here.
在本實施例中，第一壓縮單元110適於藉由驅動單元130的驅動而沿第一轉動軸線A1作動，第二壓縮單元120適於藉由驅動單元130的驅動而沿第二轉動軸線A2作動。第一轉動軸線A1與第二轉動軸線A2共軸，使驅動單元130便於同時驅動第一壓縮單元110與第二壓縮單元120作動。此外，由於第一壓縮單元110與第二壓縮單元120如上述般以共軸的方式配置，故所述流體能夠從第一壓縮單元110直線地傳遞至第二壓縮單元120而不需以曲折的方式進行傳遞，從而具有較佳的工作效率。In the present embodiment, the first compression unit 110 is adapted to be actuated along the first axis of rotation A1 by the driving of the driving unit 130, and the second compression unit 120 is adapted to be driven along the second axis of rotation A2 by the driving of the driving unit 130. Actuate. The first rotation axis A1 is coaxial with the second rotation axis A2, so that the driving unit 130 facilitates simultaneous actuation of the first compression unit 110 and the second compression unit 120. Furthermore, since the first compression unit 110 and the second compression unit 120 are disposed in a coaxial manner as described above, the fluid can be linearly transferred from the first compression unit 110 to the second compression unit 120 without being tortuous. The mode is delivered, so that it has better working efficiency.
圖4繪示圖1的壓縮設備於區域R的具體結構。請參考圖4，本實施例的第一壓縮單元110具有一第一轉軸112，第二壓縮單元120具有一第二轉軸122，壓縮設備100更包括一聯軸器140，第一轉軸112與第二轉軸122藉由聯軸器140而相連接。據此，當圖1所示的驅動單元130驅動第一壓縮單元110作動時，第二壓縮單元120可藉由第一轉軸112與第二轉軸122之連接而同時被驅動。亦即，本實施例的壓縮設備100利用聯軸器140將不同種類的壓縮單元之轉軸相連接，以整合不同種類的壓縮單元。在其他實施例中，亦可將第一轉軸112與第二轉軸122改變為連接於第一壓縮單元110與第二壓縮單元120的同一轉軸，而可省略聯軸器之設置，本發明不對此加以限制。FIG. 4 illustrates a specific structure of the compression device of FIG. 1 in a region R. Referring to FIG. 4, the first compression unit 110 of the present embodiment has a first rotating shaft 112, and the second compressing unit 120 has a second rotating shaft 122. The compression device 100 further includes a coupling 140, and the first rotating shaft 112 and the first rotating shaft 112. The two rotating shafts 122 are connected by a coupling 140. Accordingly, when the driving unit 130 shown in FIG. 1 drives the first compression unit 110 to operate, the second compression unit 120 can be simultaneously driven by the connection of the first rotating shaft 112 and the second rotating shaft 122. That is, the compression apparatus 100 of the present embodiment uses the coupling 140 to connect the rotation shafts of different kinds of compression units to integrate different types of compression units. In other embodiments, the first rotating shaft 112 and the second rotating shaft 122 may be changed to be connected to the same rotating shaft of the first compressing unit 110 and the second compressing unit 120, and the arrangement of the coupling may be omitted, and the present invention does not Limit it.
請參考圖1，本實施例的第一壓縮單元110連接於驅動單元130與第二壓縮單元120之間。然本發明不以此為限，以下藉由圖式對此舉例說明。圖5是本發明另一實施例的壓縮設備的示意圖。在圖5的壓縮設備200中，第一壓縮單元210、第二壓縮單元220、驅動單元230、入口端E1’、出口端E2’的作用方式類似圖1的第一壓縮單元110、第二壓縮單元120、驅動單元130、入口端E1、出口端E2的作用方式，於此不再贅述。壓縮設備200與壓縮設備100的不同處在於，驅動單元230連接於第一壓縮單元210與第二壓縮單元220之間。Referring to FIG. 1 , the first compression unit 110 of the embodiment is connected between the driving unit 130 and the second compression unit 120 . However, the present invention is not limited thereto, and the following is exemplified by the drawings. Figure 5 is a schematic illustration of a compression device in accordance with another embodiment of the present invention. In the compression device 200 of FIG. 5, the first compression unit 210, the second compression unit 220, the drive unit 230, the inlet end E1', and the outlet end E2' function in a similar manner to the first compression unit 110 of FIG. The mode of operation of the unit 120, the driving unit 130, the inlet end E1, and the outlet end E2 will not be described herein. The compression device 200 differs from the compression device 100 in that the drive unit 230 is coupled between the first compression unit 210 and the second compression unit 220.
綜上所述，本發明將不同種類的壓縮單元整合於單一壓縮設備，以結合不同種類壓縮機的優點。具體而言，第一壓縮單元可為結構強度較高的螺桿式壓縮單元，而第二壓縮單元可為較不易內漏而容積效率較高的渦卷式壓縮單元。當利用第一壓縮單元進行第一階段壓縮時，若進入第一壓縮單元的部分流體(如冷媒)非預期地為液態並在第一壓縮單元內氣化而瞬間膨脹，則第一壓縮單元可藉其高結構強度而避免因流體瞬間膨脹而遭受破壞。此外，當利用第二壓縮單元進行第二階段壓縮時，進入第二壓縮單元的流體因已進行過第一階段壓縮而具有較大壓力，第二壓縮單元可藉其不易內漏的特性而避免流體因壓力較大而產生內漏。藉此，可使壓縮設備具有良好的壓縮效能，並提升壓縮設備的耐用性。 In summary, the present invention integrates different types of compression units into a single compression device to combine the advantages of different types of compressors. Specifically, the first compression unit may be a screw compression unit having a higher structural strength, and the second compression unit may be a scroll compression unit that is less susceptible to internal leakage and has higher volumetric efficiency. When the first stage compression is performed by the first compression unit, if a part of the fluid (such as a refrigerant) entering the first compression unit is undesirably liquid and instantaneously expanded by gasification in the first compression unit, the first compression unit may By virtue of its high structural strength, it is prevented from being damaged by the instantaneous expansion of the fluid. In addition, when the second compression unit performs the second-stage compression, the fluid entering the second compression unit has a large pressure due to the first-stage compression, and the second compression unit can be avoided by the characteristic of not easily leaking. The fluid creates an internal leak due to the high pressure. Thereby, the compression device can have good compression performance and improve the durability of the compression device.
雖然本發明已以實施例揭露如上，然其並非用以限定本發明，任何所屬技術領域中具有通常知識者，在不脫離本發明的精神和範圍內，當可作些許的更動與潤飾，故本發明的保護範圍當視後附的申請專利範圍所界定者為準。Although the present invention has been disclosed in the above embodiments, it is not intended to limit the present invention, and any one of ordinary skill in the art can make some changes and refinements without departing from the spirit and scope of the present invention. The scope of the invention is defined by the scope of the appended claims.
100、200‧‧‧壓縮設備 100,200‧‧‧Compression equipment
110、210‧‧‧第一壓縮單元 110, 210‧‧‧ first compression unit
112‧‧‧第一轉軸 112‧‧‧First shaft
120、220‧‧‧第二壓縮單元 120, 220‧‧‧Second compression unit
122‧‧‧第二轉軸 122‧‧‧second shaft
130、230‧‧‧驅動單元 130, 230‧‧‧ drive unit
140‧‧‧聯軸器 140‧‧‧Coupling
A1‧‧‧第一轉動軸線 A1‧‧‧first axis of rotation
A2‧‧‧第二轉動軸線 A2‧‧‧second axis of rotation
E1、E1’‧‧‧入口端 E1, E1’‧‧‧ entrance end
E2、E2’‧‧‧出口端 E2, E2’‧‧‧export end
R‧‧‧區域 R‧‧‧ area
圖1是本發明一實施例的壓縮設備的示意圖。 圖2是圖1的壓縮設備與習知雙級壓縮機的耗電量的比較圖。 圖3是圖1的壓縮設備與習知雙級壓縮機的性能係數(COP)的比較圖。 圖4繪示圖1的壓縮設備於區域R的具體結構。 圖5是本發明另一實施例的壓縮設備的示意圖。1 is a schematic diagram of a compression device in accordance with an embodiment of the present invention. 2 is a graph comparing the power consumption of the compression apparatus of FIG. 1 with a conventional two-stage compressor. 3 is a graph comparing the coefficient of performance (COP) of the compression apparatus of FIG. 1 with a conventional two-stage compressor. FIG. 4 illustrates a specific structure of the compression device of FIG. 1 in a region R. Figure 5 is a schematic illustration of a compression device in accordance with another embodiment of the present invention.
Claims (20)
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TW105111428A TWI630359B (en) | 2016-04-13 | 2016-04-13 | Compressor apparatus |
| CN201610339460.6A CN107288883A (en) | 2016-04-13 | 2016-05-20 | Compression apparatus |
| JP2016153096A JP6594270B2 (en) | 2016-04-13 | 2016-08-03 | Compression device |
| EP17163466.0A EP3232063A1 (en) | 2016-04-13 | 2017-03-29 | Compression apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| TW105111428A TWI630359B (en) | 2016-04-13 | 2016-04-13 | Compressor apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| TW201736787A TW201736787A (en) | 2017-10-16 |
| TWI630359B true TWI630359B (en) | 2018-07-21 |
Family
ID=58464229
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| TW105111428A TWI630359B (en) | 2016-04-13 | 2016-04-13 | Compressor apparatus |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3232063A1 (en) |
| JP (1) | JP6594270B2 (en) |
| CN (1) | CN107288883A (en) |
| TW (1) | TWI630359B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI715330B (en) * | 2019-12-04 | 2021-01-01 | 復盛股份有限公司 | Two-stage compressor |
| CN115126695A (en) * | 2021-03-25 | 2022-09-30 | 开利公司 | Two-stage screw compressor and air conditioning system |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008130358A1 (en) * | 2007-04-24 | 2008-10-30 | Carrier Corporation | Transcritical refrigerant vapor compression system with charge management |
| CN103649496A (en) * | 2011-05-06 | 2014-03-19 | 格林·埃文斯 | A hot-air engine |
| US20140241909A1 (en) * | 2013-02-26 | 2014-08-28 | Emerson Climate Technologies, Inc. | System Including High-Side and Low-Side Compressors |
| TW201510204A (en) * | 2013-06-04 | 2015-03-16 | Du Pont | Use of alkyl perfluoroalkene ethers and mixtures thereof in high temperature heat pumps |
Family Cites Families (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS51123211U (en) * | 1975-04-02 | 1976-10-06 | ||
| JPS5288056U (en) * | 1975-12-26 | 1977-07-01 | ||
| JP2529315B2 (en) * | 1987-12-23 | 1996-08-28 | 株式会社日立製作所 | 2-stage screw compressor |
| WO1997016647A1 (en) * | 1995-11-02 | 1997-05-09 | Aaf-Mcquay Incorporated | Improved compressor arrangement and method of working the same |
| JP2001207984A (en) * | 1999-11-17 | 2001-08-03 | Teijin Seiki Co Ltd | Evacuation device |
| JP3903409B2 (en) * | 2000-03-29 | 2007-04-11 | 三菱電機株式会社 | Two-stage compression refrigerator |
| JP2003129961A (en) * | 2001-10-25 | 2003-05-08 | Hitachi Ltd | Compressor for fuel cell |
| JP2004036942A (en) * | 2002-07-01 | 2004-02-05 | Takeo Saito | Volumetric rankine engine |
| JP3966547B2 (en) * | 2002-10-31 | 2007-08-29 | 株式会社前川製作所 | Screw-type multistage compressor switchable between multistage compression and single-stage compression, and refrigeration / cooling system using the same |
| US7189066B2 (en) * | 2004-05-14 | 2007-03-13 | Varian, Inc. | Light gas vacuum pumping system |
| WO2007000815A1 (en) * | 2005-06-29 | 2007-01-04 | Mayekawa Mfg. Co., Ltd | Oil supply method and device for two-stage screw compressor, and method of operating refrigeration device |
| JP2009097486A (en) * | 2007-10-19 | 2009-05-07 | Mitsubishi Heavy Ind Ltd | Compressor |
| JP5595324B2 (en) * | 2011-04-06 | 2014-09-24 | 株式会社日本自動車部品総合研究所 | Compressor |
| GB201122142D0 (en) * | 2011-12-21 | 2012-02-01 | Venus Systems Ltd | Centrifugal compressors |
| CN103352727B (en) * | 2012-07-09 | 2016-08-24 | 摩尔动力(北京)技术股份有限公司 | Hybrid air work system and use its dynamical system |
| CN202947373U (en) * | 2012-11-15 | 2013-05-22 | 福建雪人压缩机科技有限公司 | Screw rod expansion vortex type compressor |
| CN104806525A (en) * | 2014-03-13 | 2015-07-29 | 摩尔动力(北京)技术股份有限公司 | Internal combustion air compressor provided with boundary-variable fluid mechanisms |
| CN104792051B (en) * | 2015-04-07 | 2017-11-17 | 特灵空调系统(中国)有限公司 | Multiple compression refrigerant-cycle systems and its control method |
| CN204961300U (en) * | 2015-07-10 | 2016-01-13 | 金鑫 | Unit doublestage frequency conversion helical -lobe compressor with adjustable inner volume compares |
| CN105257516A (en) * | 2015-11-17 | 2016-01-20 | 晗森机械（上海）有限公司 | Compressor with screw and centrifugal impeller being connected in series |
-
2016
- 2016-04-13 TW TW105111428A patent/TWI630359B/en active
- 2016-05-20 CN CN201610339460.6A patent/CN107288883A/en active Pending
- 2016-08-03 JP JP2016153096A patent/JP6594270B2/en active Active
-
2017
- 2017-03-29 EP EP17163466.0A patent/EP3232063A1/en not_active Withdrawn
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008130358A1 (en) * | 2007-04-24 | 2008-10-30 | Carrier Corporation | Transcritical refrigerant vapor compression system with charge management |
| CN103649496A (en) * | 2011-05-06 | 2014-03-19 | 格林·埃文斯 | A hot-air engine |
| US20140241909A1 (en) * | 2013-02-26 | 2014-08-28 | Emerson Climate Technologies, Inc. | System Including High-Side and Low-Side Compressors |
| TW201510204A (en) * | 2013-06-04 | 2015-03-16 | Du Pont | Use of alkyl perfluoroalkene ethers and mixtures thereof in high temperature heat pumps |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017190769A (en) | 2017-10-19 |
| TW201736787A (en) | 2017-10-16 |
| CN107288883A (en) | 2017-10-24 |
| JP6594270B2 (en) | 2019-10-23 |
| EP3232063A1 (en) | 2017-10-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8381538B2 (en) | Heat pump with intercooler | |
| US8316657B2 (en) | Refrigerant system and control method | |
| CN1670448A (en) | Refrigerating machine | |
| EP3425309B1 (en) | Air conditioning apparatus | |
| US10254013B2 (en) | Two-stage rotary compressor and refrigeration cycle device having same | |
| TWI630359B (en) | Compressor apparatus | |
| CN112840163A (en) | Refrigeration cycle device | |
| CN102588285B (en) | Compressor and air conditioner including same | |
| KR101250084B1 (en) | Two-stage compressor and heat pump apparatus | |
| CN204646663U (en) | Multiscrew compressor | |
| CN215062958U (en) | High-efficiency direct-current frequency-conversion cascade hot water unit | |
| US20220325715A1 (en) | Scroll compressor with economizer injection | |
| Lin et al. | The different types of cooling compressors | |
| US10309704B2 (en) | Compressor with an oil separator between compressing stages | |
| CN107228070A (en) | Compressor and the refrigeration system with it | |
| US20220316477A1 (en) | Compressor and Air Conditioning System | |
| CN210564945U (en) | Novel refrigeration compressor | |
| CN208268066U (en) | A kind of second level single screw compressor group for process gas compression | |
| CN206972526U (en) | Compressor and there is its refrigeration system | |
| US10619635B2 (en) | Scallop step for a scroll compressor | |
| US11674512B2 (en) | Two-stage screw compressor and air conditioning system | |
| JP5910263B2 (en) | Refrigeration cycle equipment | |
| CN104110377A (en) | Double-stage enthalpy-adding rotary compressor, air-conditioner and heat-pump water heater | |
| CN112361632A (en) | Refrigeration system, control method thereof and refrigeration equipment | |
| CN108035881A (en) | A kind of two level single screw compressor group for process gas compression |