TWM635271U - Reciprocating compressor - Google Patents
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Description
本創作係有關於一種壓縮機,尤指一種往復式壓縮機。The invention relates to a compressor, especially a reciprocating compressor.
一般來說,往復式壓縮機是一種由曲柄軸帶動活塞做上下位移的壓縮機,其活塞在位移時會使得氣缸內的容積發生變化,以完成壓縮過程。更具體地,往復式壓縮機在其氣缸體兩端的高壓段、低壓段之間設置平衡腔,以降低高、低壓段之壓力差。Generally speaking, a reciprocating compressor is a compressor in which the crankshaft drives the piston to move up and down. When the piston is displaced, the volume in the cylinder will change to complete the compression process. More specifically, a reciprocating compressor is provided with a balance chamber between the high-pressure section and the low-pressure section at both ends of the cylinder block to reduce the pressure difference between the high-pressure section and the low-pressure section.
然而,因為壓縮機之壓縮過程中會讓平衡腔之壓力差過大而導致低壓段和高壓段氣體洩漏至平衡腔,從而影響壓縮效率。However, during the compression process of the compressor, the pressure difference in the balance chamber will be too large, resulting in gas leakage from the low-pressure section and the high-pressure section to the balance chamber, thereby affecting the compression efficiency.
如此,如何研發出一種解決方案以精進上述所努力之方向,實乃相關業者目前刻不容緩之一重要課題。In this way, how to develop a solution to improve the above-mentioned direction of efforts is really an important issue that the relevant industry should not delay at present.
本創作提出一種往復式壓縮機,用以解決先前技術的問題。This creation proposes a reciprocating compressor to solve the problems of the prior art.
依據本創作之一實施方式,往復式壓縮機包含一氣缸體組件、一往復組件與一外部管線。氣缸體組件由一高壓級氣缸件和一低壓級氣缸件所相接而成。高壓級氣缸件具有一第一進氣口、一第一排氣口以及一連通第一進氣口及第一排氣口之高壓級內腔。低壓級氣缸件具有一第二進氣口、一連通第二進氣口之第二排氣口以及一連通高壓級內腔、第二進氣口及第二排氣口之低壓級內腔。外部管線之兩端分別連接氣缸體組件,且外部管線分別連通第二排氣口及第一進氣口。往復組件可往復地位於該氣缸體組件內,包含一高壓級活塞部、一低壓級活塞部與一活塞杆。高壓級活塞部位於高壓級內腔內。低壓級活塞部位於低壓級內腔內,並與高壓級活塞部之間定義出一平衡腔。高壓級活塞部與低壓級活塞部同軸固設於活塞杆上,且活塞杆之一部分從低壓級氣缸件之一端伸出氣缸體組件。According to an embodiment of the present invention, a reciprocating compressor includes a cylinder block assembly, a reciprocating assembly, and an external pipeline. The cylinder block assembly is formed by connecting a high-pressure cylinder part and a low-pressure cylinder part. The high-pressure stage cylinder part has a first air inlet, a first exhaust port and a high-pressure stage inner cavity communicating with the first air inlet and the first exhaust port. The low-pressure stage cylinder part has a second air inlet, a second exhaust port connected to the second air inlet, and a low-pressure stage inner chamber connected to the high-pressure stage inner chamber, the second air inlet and the second exhaust port. Both ends of the external pipeline are respectively connected to the cylinder block assembly, and the external pipeline is respectively connected to the second exhaust port and the first air intake port. The reciprocating component is reciprocally located in the cylinder body component, and includes a high-pressure piston part, a low-pressure piston part and a piston rod. The high-pressure stage piston portion is located in the high-pressure stage inner cavity. The low-pressure stage piston part is located in the low-pressure stage inner chamber, and defines a balance chamber with the high-pressure stage piston part. The high-pressure piston part and the low-pressure piston part are coaxially fixed on the piston rod, and a part of the piston rod extends out of the cylinder block assembly from one end of the low-pressure cylinder.
依據本創作一或複數個實施例,上述之往復式壓縮機更包含一通腔流道,通腔流道與氣缸體組件連通且對應設置,且連通平衡腔。According to one or more embodiments of the present invention, the above-mentioned reciprocating compressor further includes a through-chamber flow channel, which communicates with the cylinder block assembly and is arranged correspondingly, and communicates with the balance chamber.
依據本創作一或複數個實施例,在上述之往復式壓縮機中,內部流道之一端連通平衡腔,另一端連通進氣管並透過第二進氣口連通低壓級內腔。 According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, one end of the internal passage communicates with the balance cavity, and the other end communicates with the intake pipe and the inner chamber of the low-pressure stage through the second intake port.
依據本創作一或複數個實施例,在上述之往復式壓縮機中,進氣管用以將一第一段壓縮氣體或一外部氣源引入氣缸體組件內。 According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the intake pipe is used to introduce a first-stage compressed gas or an external gas source into the cylinder block assembly.
依據本創作一或複數個實施例,在上述之往復壓縮機中,通腔流道為一外部流道,外部流道之一端與氣缸體組件連接,且外部流道透過低壓級氣缸件連通平衡腔。 According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the through-cavity flow channel is an external flow channel, one end of the external flow channel is connected to the cylinder block assembly, and the external flow channel is communicated and balanced through the low-pressure stage cylinder parts cavity.
依據本創作一或複數個實施例,在上述之往復式壓縮機中,外部流道的另一端與外部管線連通。 According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the other end of the external flow channel communicates with the external pipeline.
依據本創作一或複數個實施例,在上述之往復壓縮機中,外部流道用以將一外部氣源引入氣缸體組件內。 According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the external flow channel is used to introduce an external air source into the cylinder block assembly.
依據本創作一或複數個實施例,在上述之往復壓縮機中,外部氣源的壓力小於或等於低壓級內腔的氣體壓力,且低壓級內腔的氣體壓力小於高壓級內腔的氣體壓力。 According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the pressure of the external gas source is less than or equal to the gas pressure of the inner cavity of the low-pressure stage, and the gas pressure of the inner cavity of the low-pressure stage is lower than the gas pressure of the inner cavity of the high-pressure stage .
依據本創作一或複數個實施例,在上述之往復式壓縮機中,往復式壓縮機為二段往復式壓縮機或三段往復式壓縮機。 According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the reciprocating compressor is a two-stage reciprocating compressor or a three-stage reciprocating compressor.
依據本創作一或複數個實施例,在上述之往復式壓縮機中,低壓級氣缸件為第一段壓縮氣缸,高壓級氣缸件為第二段壓縮氣缸。According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the low-pressure stage cylinder part is the first-stage compression cylinder, and the high-pressure stage cylinder part is the second-stage compression cylinder.
依據本創作一或複數個實施例,在上述之往復式壓縮機中,低壓級氣缸件為第二段壓縮氣缸,高壓級氣缸件為第三段壓縮氣缸。According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, the low-pressure stage cylinder part is the second-stage compression cylinder, and the high-pressure stage cylinder part is the third-stage compression cylinder.
依據本創作一或複數個實施例,在上述之往復式壓縮機中,外部管線上設有用以降溫的一冷卻器。According to one or more embodiments of the present invention, in the above-mentioned reciprocating compressor, a cooler for lowering the temperature is provided on the external pipeline.
如此,透過以上所述架構,往復式壓縮機透過引入一壓縮氣體或一外部氣源,以降低平衡腔內之壓力差,藉此降低低壓級氣缸件和高壓級氣缸件內的氣體流至平衡腔的洩漏量,並同時透過通腔流道回收洩漏的壓縮氣體,進而改善往復式壓縮機之壓縮效率。In this way, through the above structure, the reciprocating compressor introduces a compressed gas or an external air source to reduce the pressure difference in the balance chamber, thereby reducing the gas flow in the low-pressure stage cylinder part and the high-pressure stage cylinder part to balance The leakage of the cavity is improved, and the leaked compressed gas is recovered through the flow channel of the cavity, thereby improving the compression efficiency of the reciprocating compressor.
以上所述僅係用以闡述本創作所欲解決的問題、解決問題的技術手段、及其產生的功效等等,本創作之具體細節將在下文的實施方式及相關圖式中詳細介紹。The above description is only used to explain the problem to be solved by this creation, the technical means to solve the problem, and its effects, etc. The specific details of this creation will be introduced in detail in the following implementation methods and related drawings.
以下將以圖式揭露本創作之複數實施方式,為明確說明起見,許多實務上的細節將在以下敘述中一併說明。然而,熟悉本領域之技術人員應當瞭解到,在本創作部分實施方式中,這些實務上的細節並非必要的,因此不應用以限制本創作。此外,為簡化圖式起見,一些習知慣用的結構與元件在圖式中將以簡單示意的方式繪示之。另外,為了便於讀者觀看,圖式中各元件的尺寸並非依實際比例繪示。The following will disclose multiple implementations of this creation with diagrams. For the sake of clarity, many practical details will be described together in the following description. However, those skilled in the art should understand that in some implementations of the present invention, these practical details are not necessary, and thus should not be used to limit the present invention. In addition, for the sake of simplifying the drawings, some well-known structures and components will be shown in a simple and schematic manner in the drawings. In addition, for the convenience of readers, the size of each element in the drawings is not drawn according to actual scale.
第1圖與第2圖分別為本創作第一實施方式之往復式壓縮機10的連續操作示意圖。如第1圖至第2圖所示, 此往復式壓縮機10包含氣缸體組件100、往復組件200與外部管線300。FIG. 1 and FIG. 2 are schematic diagrams of continuous operation of the reciprocating
氣缸體組件100,由高壓級氣缸件110和低壓級氣缸件120相接而成。在本實施例中,高壓級氣缸件110和低壓級氣缸件120沿軸向L依序排列。高壓級氣缸件110之內側設有高壓級內腔111,且高壓級氣缸件110遠離低壓級氣缸件120之一端設有第一進氣口112與第一排氣口113,其中高壓級內腔111連通第一進氣口112及第一排氣口113,且第一進氣口112及第一排氣口113設置於高壓級內腔111的同一側。第一進氣口112和第一排氣口113可分別具有進氣閥I及排氣閥E,用以控制並調節流體進入和排出高壓級內腔111。此外,更可依實際工況設計需求,將第一進氣口112及第一排氣口113設置於高壓級內腔111的任二相異側;亦可將第一進氣口112及第一排氣口113僅設置進氣閥I或排氣閥E其中之一,也可以皆設置進氣閥I或排氣閥E,或是進氣閥I和排氣閥E兩者皆不設置。The
低壓級氣缸件120之內側設有低壓級內腔121,且低壓級氣缸件120遠離高壓級氣缸件110之一端設有第二進氣口122與第二排氣口123,其中低壓級內腔121連通第二進氣口122及第二排氣口123,且第二進氣口122及第二排氣口123分別設置於低壓級內腔121的相對兩側。第二進氣口122和第二排氣口123可分別具有進氣閥I及排氣閥E,用以控制並調節流體進入和排出低壓級內腔121。此外,更可依實際工況設計需求,將第二進氣口122及第二排氣口123設置於低壓級內腔121的同一側或任相異兩側;亦可將第二進氣口122及第二排氣口123僅設置進氣閥I或排氣閥E,或是進氣閥I和排氣閥E兩者皆不設置。此外,在本實施例中,低壓級內腔121與高壓級內腔111彼此直接連通,且低壓級內腔121之容積大於高壓級內腔111之容積;第一進氣口112與第二進氣口122至少一者具有進氣閥I,而第一排氣口113與第二排氣口123至少一者具有排氣閥E,或是進氣閥I和排氣閥E兩者皆不設置,然而,本創作不限於此。The inner side of the low-pressure
往復組件200可往復地位於氣缸體組件100內,且往復組件200位於高壓級內腔111及低壓級內腔121內。往復組件200包含高壓級活塞部210、低壓級活塞部220與活塞杆230,其中低壓級活塞部220之體積大於高壓級活塞部210之體積,高壓級活塞部210可往復滑移於高壓級內腔111的內壁,且低壓級活塞部220可往復滑移於低壓級內腔121的內壁。其中,低壓級活塞部220與高壓級活塞部210沿活塞杆230長軸方向彼此間隔配置,更具體地,低壓級活塞部220與高壓級活塞部210之間的容積定義出一平衡腔240。具體說明,平衡腔240可接收從高壓級內腔111或低壓級內腔121所洩漏之氣體,而於本實施例中,平衡腔240更可透過通腔流道140接收往復式壓縮機10的任一段壓縮氣體或一外部氣源,後續會更進一步說明,在此並不贅述。The
此外,高壓級活塞部210與低壓級活塞部220同軸固設於活塞杆230上,其一部分從低壓級氣缸件120之一端伸出氣缸體組件100之外。更具體地,活塞杆230之長軸方向與上述軸向L平行,且活塞杆230依序穿過低壓級活塞部220、平衡腔240與高壓級活塞部210。於本實施例中,高壓級活塞部210、低壓級活塞部220與活塞杆230組合為一級差式活塞組件,往復式壓縮機10為三段往復式壓縮機,其中低壓級氣缸件120為第二段壓縮氣缸,高壓級氣缸件110為第三段壓縮氣缸;此外,更可因應不同機型設計,將往復式壓縮機10設計為二段往復式壓縮機,其中低壓級氣缸件120為第一段壓縮氣缸,高壓級氣缸件110為第二段壓縮氣缸;或是將往復式壓縮機10設計為其他機型多級往復式壓縮機以因應不同工況需求,本創作不限於此。此外,往復組件200上不具有任何氣閥,其中低壓級活塞部220上不具有任何氣閥,故,低壓級活塞部220不致刻意或主動釋放平衡腔240內之氣體至低壓級內腔121;同理,高壓級活塞部210亦是如此。In addition, the high-
在本實施例中,外部管線300位於氣缸體組件100之外部,其兩端分別連接第二排氣口123及第一進氣口112,外部管線300例如為流體管路,然而,外部管線300不限其表現形式。In this embodiment, the
如第1圖與第2圖所示,往復式壓縮機10更包含一通腔流道140。通腔流道140與氣缸體組件100連通且對應設置,並且連通平衡腔240,用以輸入氣體至平衡腔240內和排出平衡腔240內的氣體。更進一步說明,通腔流道140為一開設於低壓級氣缸件120之側壁內部之內部流道141,內部流道141位於低壓級氣缸件120之一側且與平衡腔240對應設置。其中氣缸體組件100更包含一進氣管130,進氣管130之一端連接低壓級氣缸件120,使進氣管130依序透過內部流道141及第二進氣口122連通低壓級內腔121。此外,內部流道141之一端連通平衡腔240,另一端透過第二進氣口122連通低壓級內腔121。As shown in FIG. 1 and FIG. 2 , the
除此之外,進氣管130可引入往復式壓縮機10的第一段壓縮氣體或外部氣源透過內部流道141進入平衡腔240內,使低壓級氣缸件120內的氣體壓力與平衡腔240內的氣體壓力差值下降,高壓級氣缸件110內的氣體壓力與平衡腔240內的氣體壓力差值下降,降低平衡腔240內之壓力差,使往復式壓縮機10於運轉時,藉此降低低壓級氣缸件120和高壓級氣缸件110內的壓縮氣體流至平衡腔240的洩漏量,並同時透過通腔流道140回收洩漏的壓縮氣體,進而改善並提升往復式壓縮機之壓縮效率。In addition, the
更具體說明,當往復式壓縮機10為三段往復式壓縮機時,低壓級氣缸件120及高壓級氣缸件110分為第二段壓縮氣缸和第三段壓縮氣缸。此時,進氣管130可引入往復式壓縮機10的第一段壓縮氣體或外部氣源透過內部流道141進入平衡腔240內,使第二段壓縮氣缸內的氣體壓力與平衡腔240內的氣體壓力差值下降,第三段壓縮氣缸內的氣體壓力與平衡腔240內的氣體壓力差值下降,降低平衡腔240內之壓力差,大幅降低低壓級氣缸件120和高壓級氣缸件110的運轉洩漏量。其中外部氣源的壓力小於或等於低壓級內腔121的氣體(第二段壓縮氣體)壓力,且低壓級內腔121的氣體壓力小於高壓級內腔111的氣體壓力。More specifically, when the reciprocating
更進一步說明,當往復式壓縮機10為三段往復式壓縮機時,進氣管130可引入往復式壓縮機10的第一段壓縮氣體並透過內部流道141進入平衡腔240內,此時平衡腔240內部的氣體壓力由大氣壓力上升為第一段壓縮氣體的壓力,而使第二段壓縮氣缸內的氣體壓力與平衡腔240及第三段壓縮氣缸內的氣體壓力與平衡腔240內的氣體壓力差值下降,降低平衡腔240內之壓力差。此時,進氣管130於往復組件200進行往復運動時,透過內部流道141輸送第一段壓縮氣體進入平衡腔240內及第二段壓縮氣缸內。
To further illustrate, when the reciprocating
此外,進氣管130也可引入外部氣源透過內部流道141進入平衡腔240內,此時平衡腔240內部的氣體壓力由大氣壓力上升為外部氣源的氣體壓力,而使第二段壓縮氣缸內的氣體壓力與平衡腔240及第三段壓縮氣缸內的氣體壓力與平衡腔240內的氣體壓力差值下降,降低平衡腔240內之壓力差。其中,外部氣源的壓力小於或等於低壓級內腔121的氣體(第二段壓縮氣體)壓力。更進一步說明,當外部氣源與第一段壓縮氣體同時經由進氣管130引入內部流道141時,此時外部氣源的氣體壓力需小於或等於第一段壓縮氣體壓力,以避免外部氣源的氣體壓力過大而阻礙第一段壓縮氣體的引入;而當外部氣源藉由進氣管130引入內部流道141,且第一段壓縮氣體藉由低壓級氣缸件120的相異處進入低壓級內腔121時,此時外部氣源的氣體壓力則可介於第一段壓縮氣體壓力和低壓級內腔121的氣體(第二段壓縮氣體)壓力之間,亦可等於第一段壓縮氣體壓力或低壓級內腔121的氣體(第二段壓縮氣體)壓力。
In addition, the
除此之外,更可因應不同機型設計,將往復式壓縮機10設計為二段往復式壓縮機,其中低壓級氣缸件
120為第一段壓縮氣缸,高壓級氣缸件110為第二段壓縮氣缸。此時,進氣管130可引入外部氣源透過內部流道141進入平衡腔240內,使第一段壓縮氣缸內的氣體壓力與平衡腔240內的氣體壓力差值下降,第二段壓縮氣缸內的氣體壓力與平衡腔240內的氣體壓力差值下降,降低平衡腔240內之壓力差,大幅降低低壓級氣缸件120和高壓級氣缸件110的運轉洩漏量。其中外部氣源的壓力小於或等於低壓級內腔121的氣體(第一段壓縮氣體)壓力,且低壓級內腔121的氣體壓力小於高壓級內腔111的氣體壓力。
In addition, the reciprocating
更進一步說明,當往復式壓縮機10為二段往復式壓縮機時,進氣管130引入外部氣源透過內部流道141進入平衡腔240內,進氣管130於往復組件200進行往復運動時,透過內部流道141輸送外部氣體進入平衡腔240內或第一段壓氣缸內。此時平衡腔240內部的氣體壓力由大氣壓力上升為外部氣源的氣體壓力,而使第一段壓縮氣缸內的氣體壓力與平衡腔240及第二段壓縮氣缸內的氣體壓力與平衡腔240內的氣體壓力差值下降,降低平衡腔240內之壓力差。其中,外部氣源的氣體壓力小於或等於低壓級內腔121的氣體(第一段壓縮氣體)壓力,也就是外部氣源的氣體壓力則可介於大氣壓力和低壓級內腔121的氣體(第一段壓縮氣體)壓力之間,亦可等於大氣壓力或低壓級內腔121的氣體(第一段壓縮氣體)壓力。To further illustrate, when the reciprocating
接續針對往復式壓縮機10運轉時,氣缸體組件100內的氣體流動變化作詳細說明。如第1圖所示,當往復組件200從高壓級內腔111朝下移動以壓縮低壓級內腔121的氣體時,低壓級氣缸件120進行壓縮排氣程序而高壓級氣缸件110進行吸氣程序。更進一步說明,當低壓級氣缸件120進行壓縮排氣程序時,低壓級內腔121內的空間變小,使得低壓級內腔121內之氣體(暫稱第一腔內氣體)被低壓級活塞部220壓縮而使其氣體壓力升高並且從第二排氣口123排出至外部管線300,而高壓級活塞部210同軸連動向下移動,使高壓級內腔111內的空間變大,高壓級氣缸件110進行吸氣程序,使第一腔內氣體由低壓級內腔121依序流經第二排氣口123、外部管線300、第一進氣口112,最後到達高壓級內腔111內,其內之氣體暫稱第二腔內氣體;於此同時,透過往復組件200朝下移動,使平衡腔240進行吸氣程序,平衡腔240於低壓級氣缸件120內的空間變大,使得往復式壓縮機10的第一段壓縮氣體或外部氣源 (暫稱第一外部氣體)透過進氣管130進入氣缸體組件100,接著第一外部氣體透過內部流道141後進入平衡腔240內,其內之氣體暫稱第三腔內氣體。如此,由於第三腔內氣體提高了平衡腔240內之氣體壓力,能夠減少平衡腔240相對其二端內腔(即高壓級內腔111及低壓級內腔121)之壓力差,降低高壓級內腔111及低壓級內腔121內的氣體洩漏量。Next, the gas flow changes in the
如第2圖所示,當往復組件200從低壓級內腔121朝上移動以壓縮高壓級內腔111時,高壓級氣缸件110進行壓縮排氣程序,低壓級氣缸件120進行吸氣程序。更進一步說明,當高壓級活塞部210向上移動時,高壓級內腔111內的空間變小,使得高壓級內腔111內之第二腔內氣體經由第一排氣口113被送出氣缸體組件100之外,而低壓級活塞部220同軸連動向上移動,使低壓級內腔121內的空間變大,低壓級氣缸件120進行吸氣程序,使第一段壓縮氣體或外部氣源(暫稱第二外部氣體)經由進氣管130依序流經內部流道141、第二進氣口122,最後到達低壓級內腔121內;於此同時,透過往復組件200朝上移動,使平衡腔240進行排氣程序,平衡腔240於低壓級氣缸件120內的空間變小,使得第三腔內氣體從平衡腔240內排出,再經由內部流道141被送入低壓級內腔121內,並與第二外部氣體混合為上述第一腔內氣體。如此,透過重複上述第1圖及第2圖之所述動作,以讓往復組件200反覆進行氣體壓縮之工作。As shown in FIG. 2 , when the
值得一提的是,隨著往復式壓縮機10長期運轉,往復組件200的密封性會漸漸耗損,此時高壓級內腔111及低壓級內腔121內的第一腔內氣體和第二腔內氣體,會於往復運動時產生氣體洩漏,但由於本創作之平衡腔240內的低壓差的設計,使得高壓級內腔111及低壓級內腔121的洩漏量大幅減少,且藉由通腔流道140回收第三腔內氣體至低壓級內腔121的設計,可降低壓縮損耗,進而提升往復式壓縮機之壓縮效率。It is worth mentioning that, with the long-term operation of the
第3圖與第4圖分別為本創作第二實施方式之往復式壓縮機11的連續操作示意圖。如第3圖至第4圖所示,本實施方式之往復式壓縮機11與上述實施方式之往復式壓縮機10大致相同,其差異在於,通腔流道140A為一位於氣缸體組件100之外的外部流道142,外部流道142之一端與氣缸體組件100連接,且透過低壓級氣缸件120的內部設計連通平衡腔240。此外,外部流道142的另一端與外部管線300連通,使得外部管線300內的氣體可藉由外部流道142旁通流至氣缸體組件100內的平衡腔240。其中,外部流道142例如為流體管路、往復式壓縮機10的機殼孔道或二者之結合等等,然而,外部管線300不限其表現形式。其中,外部管線300上設有用以降溫的冷卻器(圖中未示),外部流道142連通外部管線300且位於冷卻器的下游處,以降低進入平衡腔240和高壓級內腔111的氣體溫度。FIG. 3 and FIG. 4 are schematic diagrams of continuous operation of the
接續針對往復式壓縮機11運轉時,氣缸體組件100內的氣體流動變化作詳細說明。如第3圖所示,當往復組件200從高壓級內腔111朝下移動以壓縮低壓級內腔121的氣體時,低壓級氣缸件120進行壓縮排氣程序而高壓級氣缸件110進行吸氣程序。更進一步說明,當低壓級氣缸件120進行壓縮排氣程序時,低壓級內腔121內的空間變小,低壓級內腔121內之所述第一腔內氣體被低壓級活塞部220壓縮而使其氣體壓力升高並且從第二排氣口123排出至外部管線300,而高壓級活塞部210同軸連動向下移動,使高壓級內腔111內的空間變大,高壓級氣缸件110進行吸氣程序,使第一腔內氣體由低壓級內腔121依序流經第二排氣口123、外部管線300、冷卻器(圖中未示)、第一進氣口112,最後到達高壓級內腔111內,其內之氣體暫稱第二腔內氣體;於此同時,透過往復組件200朝下移動,使平衡腔240進行吸氣程序,平衡腔240於低壓級氣缸件120內的空間變大,使得低壓級內腔121的第一腔內氣體透過外部管線300、冷卻器(圖中未示)和外部流道142進入氣缸體組件100,接著第一腔內氣體透過低壓級氣缸件120的內部設計進入平衡腔240內,以成為所述第三腔內氣體。如此,由於第三腔內氣體提高了平衡腔240內之氣體壓力,能夠減少平衡腔240相對其二端內腔(即高壓級內腔111及低壓級內腔121)之壓力差,降低高壓級內腔111及低壓級內腔121內的氣體洩漏。其中,第三腔內氣體壓力幾乎等於第一腔內氣體壓力,且第一腔內氣體壓力小於第二腔內氣體壓力。Next, the gas flow changes in the
如第4圖所示,當往復組件200從低壓級內腔121朝上移動以壓縮高壓級內腔111時,高壓級氣缸件110進行壓縮排氣程序,低壓級氣缸件120進行吸氣程序。更進一步說明,當高壓級活塞部210向上移動時,高壓級內腔111內的空間變小,使得高壓級內腔111內之第二腔內氣體經由第一排氣口113被送出氣缸體組件100之外,而低壓級活塞部220同軸連動向上移動,使低壓級內腔121內的空間變大,低壓級氣缸件120進行吸氣程序,使第一段壓縮氣體或外部氣源(暫稱第二外部氣體)經由第二進氣口122流入低壓級內腔121內;於此同時,透過往復組件200朝上移動,使平衡腔240進行排氣程序,平衡腔240於低壓級氣缸件120內的空間變小,使得第三腔內氣體從平衡腔240內排出,再經由外部流道142被送至外部管線300內,並與第一腔內氣體混合。如此,透過重複上述第3圖及第4圖之所述動作,以讓往復組件200反覆進行氣體壓縮之工作。As shown in FIG. 4 , when the
第5圖與第6圖分別為本創作第三實施方式之往復式壓縮機11的連續操作示意圖。如第5圖至第6圖所示,本實施方式之往復式壓縮機12與上述第二實施方式之往復式壓縮機11大致相同,通腔流道140B亦為位於氣缸體組件100之外的外部流道143,其差異在於,外部流道143引入外部氣體,外部流道143之一端與氣缸體組件100連接,而另一端與一外部氣源G(其外部氣體暫稱第三外部氣體)連通,使得第三外部氣體可透過外部流道143進入或排出氣缸體組件100的平衡腔240內;此設計更能依工況,隨時調節平衡腔240內的氣體壓力大小,更能即時調節高壓級內腔111及低壓級內腔121內的氣體洩漏量。其中,第三外部氣體壓力可小於或等於第一腔內氣體壓力,且第一腔內氣體壓力小於第二腔內氣體壓力。FIG. 5 and FIG. 6 are respectively schematic diagrams of continuous operation of the
更進一步說明,當往復式壓縮機10為三段往復式壓縮機時,此時第三外部氣體的壓力介於第一段壓縮氣體壓力和低壓級內腔121的氣體(如第二段壓縮氣體)壓力之間,亦可等於第一段壓縮氣體壓力或低壓級內腔121的氣體(如第二段壓縮氣體)壓力;而當將往復式壓縮機10設計為二段往復式壓縮機,此時第三外部氣體的壓力介於大氣壓力和低壓級內腔121的氣體(第一段壓縮氣體)壓力之間,亦可等於大氣壓力或低壓級內腔121的氣體(第一段壓縮氣體)壓力。To further illustrate, when the reciprocating
須了解到,上述這些往復式壓縮機10、11、12例如為水冷無油往復式壓縮機,其中可為兩段往復式壓縮機或三段往復式壓縮機,然而,本創作不限於此。此外,上述之進氣閥I與排氣閥E使用現有的各種氣閥;所述高壓級氣缸件110和低壓級氣缸件120的缸體可設置成立式、臥式、角度式、對稱式等任意形式,而冷卻方式可採用水冷、風冷、自然冷卻等任意冷卻方式,可採用無油或有油潤滑。It should be understood that the above-mentioned
如此,透過以上所述架構,往復式壓縮機透過引入一壓縮氣體或一外部氣源,以降低平衡腔內之壓力差,藉此降低低壓級氣缸件和高壓級氣缸件內的氣體流至平衡腔的洩漏量,並同時透過通腔流道回收洩漏的壓縮氣體,進而改善往復式壓縮機之壓縮效率。In this way, through the above structure, the reciprocating compressor introduces a compressed gas or an external air source to reduce the pressure difference in the balance chamber, thereby reducing the gas flow in the low-pressure stage cylinder part and the high-pressure stage cylinder part to balance The leakage of the cavity is improved, and the leaked compressed gas is recovered through the flow channel of the cavity, thereby improving the compression efficiency of the reciprocating compressor.
最後,上述所揭露之各實施例中,並非用以限定本創作,任何熟習此技藝者,在不脫離本創作之精神和範圍內,當可作各種之更動與潤飾,皆可被保護於本創作中。因此本創作之保護範圍當視後附之申請專利範圍所界定者為準。Finally, the embodiments disclosed above are not intended to limit this creation. Anyone who is familiar with this technique can make various changes and modifications without departing from the spirit and scope of this creation, and all of them can be protected in this creation. creation. Therefore, the scope of protection of this creation should be defined by the scope of the attached patent application.
10、11、12:往復式壓縮機10, 11, 12: Reciprocating compressors
100:氣缸體組件100: Cylinder block assembly
110:高壓級氣缸件110: High pressure cylinder parts
111:高壓級內腔111: High pressure inner cavity
112:第一進氣口112: The first air inlet
113:第一排氣口113: The first exhaust port
120:低壓級氣缸件120: Low-pressure cylinder parts
121:低壓級內腔121: Low-pressure inner cavity
122:第二進氣口122: Second air inlet
123:第二排氣口123: Second exhaust port
130:進氣管130: Intake pipe
140、140A、140B:通腔流道140, 140A, 140B: cavity flow channel
141:內部流道141: Internal runner
142、143:外部流道142, 143: external runner
200:往復組件200: Reciprocating components
210:高壓級活塞部210: High pressure piston part
220:低壓級活塞部220: Low-pressure piston part
230:活塞杆230: piston rod
240:平衡腔240: balance cavity
300:外部管線300: external pipeline
E:排氣閥E: exhaust valve
G:外部氣源G: External air source
I:進氣閥I: intake valve
L:軸向L: Axial
為讓本創作之上述和其他目的、特徵、優點與實施例能更明顯易懂,所附圖式之說明如下: 第1圖與第2圖分別為本創作第一實施方式之往復式壓縮機的連續操作示意圖; 第3圖與第4圖分別為本創作第二實施方式之往復式壓縮機的連續操作示意圖;以及 第5圖與第6圖分別為本創作第三實施方式之往復式壓縮機的連續操作示意圖。 In order to make the above-mentioned and other purposes, features, advantages and embodiments of this creation more obvious and easy to understand, the description of the accompanying drawings is as follows: Figure 1 and Figure 2 are schematic diagrams of the continuous operation of the reciprocating compressor in the first embodiment of the invention; Figure 3 and Figure 4 are schematic diagrams of the continuous operation of the reciprocating compressor of the second embodiment of the present invention; and Fig. 5 and Fig. 6 are schematic diagrams of continuous operation of the reciprocating compressor according to the third embodiment of the present invention, respectively.
10:往復式壓縮機 10: Reciprocating compressor
100:氣缸體組件 100: Cylinder block assembly
110:高壓級氣缸件 110: High pressure cylinder parts
111:高壓級內腔 111: High pressure inner cavity
112:第一進氣口 112: The first air inlet
113:第一排氣口 113: The first exhaust port
120:低壓級氣缸件 120: Low-pressure cylinder parts
121:低壓級內腔 121: Low-pressure inner cavity
122:第二進氣口 122: Second air inlet
123:第二排氣口 123: Second exhaust port
130:進氣管 130: Intake pipe
140:通腔流道 140: cavity flow channel
141:內部流道 141: Internal runner
200:往復組件 200: Reciprocating components
210:高壓級活塞部 210: High pressure piston part
220:低壓級活塞部 220: Low-pressure piston part
230:活塞杆 230: piston rod
240:平衡腔 240: balance cavity
300:外部管線 300: external pipeline
E:排氣閥 E: exhaust valve
I:進氣閥 I: intake valve
L:同軸方向 L: coaxial direction
Claims (13)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
TW111206676U TWM635271U (en) | 2022-06-23 | 2022-06-23 | Reciprocating compressor |
CN202320093597.3U CN219139280U (en) | 2022-06-23 | 2023-01-31 | Reciprocating compressor |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
TW111206676U TWM635271U (en) | 2022-06-23 | 2022-06-23 | Reciprocating compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
TWM635271U true TWM635271U (en) | 2022-12-11 |
Family
ID=85786414
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
TW111206676U TWM635271U (en) | 2022-06-23 | 2022-06-23 | Reciprocating compressor |
Country Status (2)
Country | Link |
---|---|
CN (1) | CN219139280U (en) |
TW (1) | TWM635271U (en) |
-
2022
- 2022-06-23 TW TW111206676U patent/TWM635271U/en unknown
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2023
- 2023-01-31 CN CN202320093597.3U patent/CN219139280U/en active Active
Also Published As
Publication number | Publication date |
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CN219139280U (en) | 2023-06-06 |
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