201211392 六、發明說明： 【發明所屬之技術領域】 本發明係關於一種來回作動壓縮機之餘隙穴，特別是關於 • 一種用以將螺合於餘隙活塞桿上之螺母設為經由彈菁構件 卡合之二體，可藉由無嗓嘎聲之螺合而實現穩定之動作與遠 距離操作等之新穎的改良。 【先前技術】 先前，作為一直使用之來回作動壓縮機之容量控制的方法 之一’存在餘隙穴]乍為代表性之構成，τ將專利文獻\ 所揭示之構成列舉為圖3。 即，於圖3中，具有餘隙穴3、平衡裝置6、及作動裝置(餘 隙穴之驅動部）8,並且使用油壓手段u作為致動器:二 平衡裝置6係於餘隙穴本體6G滑動自如地嵌合^活=述 7而劃分平衡室61，藉由連通路徑62而連通壓力室 衡室61，並且藉㈣1連結棒5㈣h活塞體7與第i 活塞體4連結，從而使壓力室^内之氣壓與調節室 向而導入至平衡室61;上述作動裝置8係使第 ' 向特定位㈣:而使調節室31之容積增減化。又:於欲4 少_機之容量時’藉由打開連接於汽幻内人/ ==缸1之間隙容積。於來回作動壓縮機中； 出衝私束而進入吸入衝程，殘留於汽幻内 嘴 之壓縮氣财賴，故Μ行縫之狀直至、、=積部 100129157 3 201211392 力變得低於吸人壓力為止。若增大_容積，騎吸入衝程 中膨脹氣體佔據之體積增加，吸人量按照該程度減少。於該 容量控制方式中’活塞2壓縮之氣體量本身減少，故亦可節 減消耗動力。 又，作為使用有餘隙穴之可變容量型之來回作動壓縮機， 可將專利文獻2所揭示之構成列舉為圖4。 即，圖4係表示來回作動壓縮機之主要部分之餘隙穴之剖 面圖，構成為如下：間隙調整桿43是設置於汽缸蓋41的隔 離壁41卜並具有用以閉蓋以前端側之錐形桿部43t收容活 塞之汽缸40之_穴41a，並位於使㈣穴4u與汽缸4〇 之頭侧氣體壓縮室條連通之錐形孔狀之氣體通過孔^ 内的方式’螺©並支持桿支持模具44之㈣紋，將基端侧 之螺桿桿部43s之外螺紋固著在閉蓋汽缸罩蓋41之外蓋 42,並將間隙調整桿43自桿支持模具44之突出端連結於步 進馬達45之輸出軸’藉由使該間隙調整桿43正反自如地旋 轉而於長度方向來回作動。 因此右藉由遠距離操作而使間隙容積連續地變化，則壓 :之吸人里亦連續地變化，故於製程中所需之氣體量時刻 改交之If ;兄下’亦可藉由僅對必需之氣體量進行壓縮而獲得 較大之即此效果。因此，使用有如下之裝置:以可使用致動 :子餘隙八之讀進彳亍遠距離操作之方式構成，且根據喷出 麼力等製程條件並使用測定值而如經由控制襄置 自動地喷 100129157201211392 VI. Description of the Invention: [Technical Field] The present invention relates to a clearance hole for a reciprocating compressor, and more particularly to: a nut for screwing a piston rod to a clearance piston The two members of the component can be combined to achieve a novel improvement such as stable operation and long-distance operation by screwing without a click. [Prior Art] Conventionally, as one of the methods for controlling the capacity of the reciprocating compressor that has been used all the time, there is a configuration in which a clearance hole is 代表性, and τ is a configuration disclosed in the patent document. That is, in Fig. 3, there is a clearance hole 3, a balancing device 6, and an actuating device (a driving portion of the clearance hole) 8, and a hydraulic means u is used as the actuator: the second balancing device 6 is attached to the clearance hole. The main body 6G is slidably fitted to the balance chamber 61, and the pressure chamber chamber 61 is connected by the communication path 62, and the (4) 1 connecting rod 5 (four) h piston body 7 is coupled to the i-th piston body 4, thereby The air pressure in the pressure chamber is introduced into the balance chamber 61 in the direction of the adjustment chamber. The actuator 8 is configured to increase the volume of the adjustment chamber 31 by the specific position (4). Also: when you want 4 less _ machine capacity ' by opening the gap volume connected to the Cyclone insider / == cylinder 1. In the compressor, the compressor is slammed into the suction stroke, and the compressor is left in the suction stroke. The residual gas in the cylinder of the phantom is the entanglement of the gas, so the sew is until the seam, until the product is 100129157 3 201211392. Until the pressure. If the volume is increased, the volume occupied by the inflation gas during the suction stroke is increased, and the amount of suction is reduced to this extent. In this capacity control mode, the amount of gas compressed by the piston 2 itself is reduced, so that the power consumption can be reduced. Further, as a variable-capacity back-and-forth compressor using a clearance hole, the configuration disclosed in Patent Document 2 can be referred to as FIG. That is, FIG. 4 is a cross-sectional view showing the clearance portion of the main portion of the reciprocating compressor, which is configured as follows: the gap adjusting rod 43 is provided on the partition wall 41 of the cylinder head 41 and has a front end side for closing the cover. The tapered rod portion 43t accommodates the hole 41a of the cylinder 40 of the piston, and is located in the manner of the conical hole-shaped gas passing through the hole (the fourth hole 4u and the head side gas compression chamber of the cylinder 4). The support rod supports the (four) pattern of the mold 44, and the screw rod portion 43s on the proximal end side is screwed to the outer cover 42 of the closed cylinder cover 41, and the gap adjustment rod 43 is connected from the protruding end of the rod support mold 44. The output shaft ' of the stepping motor 45 is moved back and forth in the longitudinal direction by rotating the gap adjusting lever 43 forward and backward. Therefore, the right gap is continuously changed by the remote operation, and the pressure is continuously changed in the suction, so that the amount of gas required in the process is changed at the time of If; This effect is obtained by compressing the amount of gas necessary to obtain a larger amount. Therefore, a device is used which is constructed in such a manner that the actuation can be performed by the operation of the sub-gap eight and the process is performed according to the process conditions such as the ejection force and the measured value is used, for example, via the control device. Ground spray 100129157
S 201211392 出必需量般進行控制° [先行技術文獻] [專利文獻] [專利文獻1]曰本專利特開平11-82314號公報 [專利文獻2]日本專利特開平10-122138號公報 【發明内容】 (發明所欲解決之問題） 於上述圖3之先前構成之情況下，油壓缸係因如下之原因 而使用：可藉由小致動器而輸出較大之力；及作動油之壓縮 性非常小，故不會產生因變動負重引起之振動。對於直接連 結於該汽缸之氣體壓縮室之餘隙穴之容量調節活塞(餘隙活 塞）’與向汽缸内之氣體之吸入•壓縮•喷出衝程對應之壓 力變動起作用，故較大之變動負重起作用。 又，例如，於助燃性強之氧氣用壓縮機中，較理想的是為 了避免因高壓氧引起之著火而不使用油壓之驅動方法。 又，於上述圖4之先前構成之情況下，將螺桿桿部之前端 之錐形桿部插人至_孔狀之氣體通過孔，並藉由該插入情 況而調整與餘隙穴連通之程度，但由於流人或流出穴之氣體 通道窄，故存在壓力損耗變大之缺點。 另外，雖未圖示’但於手動式之餘隙穴中，亦採用利用螺 桿式致動H之驅動。於該情況下，存在如下之虞：藉由變動 負重而螺桿面受到敲擊，從而成為破損之原因。為了避免該 100129157 5 201211392 情形’手動式係呈如下構造 點，對其他鎖定螺母進Γ㈣纟；：°束塞之移動之時間 伽#避免因彻變動負重敲 厂干 之破損。然、而’為了藉由遠距離操作使2個螺 ==需要複雜之機構，從而於設置空間及成本方 面存在問>€’ 提高城之可靠性。 因此’本發明之目的在於提供一種將螺合於 螺=為經由彈菁構件卡合之二體，可_ ::現穩定之動作與遠距離操作等之來回作動壓二 (解決問題之手段） 本發明之來回作動壓縮機之餘隙穴係包括有：汽紅 成有吸及嘴出口且内設有活塞；上侧氣體麗縮室及下 氣體壓縮室’係於上述汽缸内藉由上述活塞而分割；餘隙穴 本體’係設置於上述汽缸之上部讀上述上側氣朗縮室連 通並且具有穴室及穴背麈室；上述餘隙穴本體内之餘隙活 塞；及驅動體，用以使上述餘隙活塞滑動，藉由上述餘隙活 塞之滑動而使與上述上職體壓魅連通之上述穴室之容 積可變者具有設置於上述餘訪塞且具有外螺紋並^ 藉由防轉器保持為非旋轉狀態之桿、螺合於上述外螺紋之螺 母、及形紅述螺母且經由彈簧構件相互向反方向施力而十、 合之第卜第2螺母部之構成’又’呈具有設置於上述螺母 之外周之第1齒輪、及設置於上述驅動體且與上述第！齒輪 6 100129157In the case of the above-mentioned Japanese Patent Application Laid-Open No. Hei. No. Hei. No. Hei. No. Hei. 】 (Problem to be Solved by the Invention) In the case of the previous configuration of Fig. 3 above, the hydraulic cylinder is used for the following reasons: a large force can be output by a small actuator; and compression of the oil is performed The sex is very small, so there is no vibration caused by the variable load. The pressure-adjusting piston (retaining piston) of the clearance chamber directly connected to the gas compression chamber of the cylinder acts on the pressure fluctuation corresponding to the suction, compression, and discharge stroke of the gas in the cylinder, so the larger variation The weight is working. Further, for example, in a compressor for oxygen which is highly flammable, it is preferable to use a driving method for avoiding ignition due to high pressure oxygen. Further, in the case of the above-described configuration of FIG. 4, the tapered rod portion at the front end of the screw shaft portion is inserted into the hole-shaped gas passage hole, and the degree of communication with the clearance hole is adjusted by the insertion condition. However, since the gas passage of the flowing person or the outflow hole is narrow, there is a disadvantage that the pressure loss becomes large. Further, although not shown in the figure, the driving by the screw type actuation H is also employed in the manual clearance. In this case, there is a problem that the screw surface is knocked by changing the load, which causes damage. In order to avoid the situation of the '101129157 5 201211392' manual, the following construction points are made, and the other locking nuts are inserted into the 锁定 (4) 纟;: ° The time of the movement of the tamping gamma # avoids the damage of the factory due to the change of the load. However, in order to make two screws == require a complicated mechanism by remote operation, there is a problem in the installation space and cost. Therefore, the object of the present invention is to provide a two-body that is screwed to a screw, which is a card that is engaged via an elasticite member, and can be used to move back and forth between the action of the stable operation and the remote operation (the means to solve the problem). The clearance system of the back and forth actuating compressor of the present invention comprises: a steam red into a suction and a nozzle outlet and a piston is disposed therein; the upper gas retracting chamber and the lower gas compression chamber are connected to the cylinder by the piston And the separation; the cavity body is disposed on the upper portion of the cylinder to read the upper side of the gas chamber and has a chamber and a pocket chamber; the clearance piston in the space cavity; and the driving body The clearance piston is slid, and the volume of the chamber that communicates with the upper body pressure is made variable by the sliding of the clearance piston, and is provided on the outer plug and has an external thread and is prevented by The rod held in the non-rotating state, the nut screwed to the external thread, and the nut of the shape described above are biased in opposite directions via the spring member, and the composition of the second nut portion is further Presented in the above The mother outside circumferential first gear, and is provided in the driving body and the first and! Gears 6 100129157
201211392 乂。之第2齒輪’且藉由上述驅動體之驅動進行上述桿及餘 隙活塞之移動之構成，Λ，呈作為上述餘隙活塞之活塞背 壓’使上述汽紅之吸人壓與噴出壓之中間之中間壓發揮作用 之構成’又’呈作為上述餘隙活塞之活塞背壓，使上述汽缸 之吸入壓發揮作用之構成，又，呈上述彈簧構件由盤彈箸所 構成之構成。 (發明效果） 本發明之來回作動壓縮機之餘隙穴係如上所述般構成，故 可獲得如下之效果。 即、，於包括形成有吸入口及喷出口且内設有活塞之汽缸、 :上述内藉由上述活塞而分割之上侧氣體㈣室及下 側^體H、設置於上述汽缸之上部且與上述上側氣體廢 2室連通並且具有穴室及穴隸室之餘隙穴本體、上述餘隙 二本體内之餘隙活塞、及用以使上述餘隙活塞滑動之驅動 ’且藉由上述餘隙活塞之滑動而使與上述上側氣體壓縮室 = 上述穴室之容積可變的來回作動壓縮機之餘隙穴 保梏置於上述餘隙活塞且具有外螺紋並且藉由防轉器 上'螺合^述外螺紋之螺母、及形成 工^母且經由彈簧構件相互向反方向施力而卡合之第 Ο 先對内2蟫^’自^2個料利^料構件，並預 變動負，故即便於螺桿之咬合部μ聲消失而 重作用於桿上’亦不會產生因敲擊螺桿面弓丨起之破 100129157 201211392 損又餘隙活塞之前進及後退係藉由使汽缸側之内螺紋正 轉及反轉而進行。又’於餘隙活塞停止之狀態下，彈簧構件 a&即便變動負該作用，螺桿面亦始 終向方向推壓而摩擦力起仙，從而不存在餘隙活塞隨意 地移動之情形。 又具有η又置於上述螺母之外周之第丨齒輪、及設置於上 述驅動體且與上述第丨絲咬合之第2錄，且藉由上述驅 動體之驅動而進行上述桿及餘隙活塞之移動，藉此使用驅動 體使齒輪旋轉而使餘隙活塞前進•後退，藉此可藉由遠距離 操作而變更_容積。若如取人製義之輸人信號，並以成 為必需之氣體量之方式進行餘隙活塞之前進.後退般構成控 制裝置，則可自動地進行壓縮機之容量調節。 又，作用於餘隙活塞之變動負重除壓縮機之吸入·喷出壓 力、零件重量外，作用於餘隙活塞之穴背壓室之背壓較大地 產生影響。於使汽缸内之平均壓力作用於穴背壓室之情況 下，將汽缸内與穴背壓室經由孔口等節流器連接。然而，該 情形亦可藉由β又置自餘隙活塞之前面連通於穴背壓室之細 穴而獲得相同之作用，故構造變簡單。另一方面，作用於餘 隙活塞之負重之振幅於上下方向大幅變化，故需要使作用於 螺母間之彈力變大。另外，具有如下之缺點：為了使餘隙活 塞移動，使螺母旋轉所需之轉矩亦變大。 於使吸入壓力作用於穴背壓室之情況下，作為負重之振幅 100129157 201211392 亦與上述相等’但因重量產生之負重相對於壓力負重而言相 對較J藉此向上之負重為主且向下之負重微小。因此，藉 由彈簧構件發揮作用之彈力為較小者即可，且亦可縮小使螺 母旋轉所需之轉矩。 【實施方式】 [實施例] 以下’連同圖式一併對本發明之來回作動壓縮機之餘隙穴 之較佳的實施形態進行說明。 再者，對與圖3相同或相等部分使用相同之符號進行說 明。 於圖1中，在壓縮機之框架1A上設置有汽缸丨，經由活 塞棒2c驅動之活塞2於汽缸丨内來回作動。該汽缸丨係於 活塞2之上面與下面之兩側對氣體進行壓縮之雙動式，在上 側氣體壓縮室2a及下側氣體壓縮室沘，分別設置有吸入閥 12a、12b及喷出閥14a、14b。該等汽缸閥（吸入閥12a、12b 及喷出閥14a、14b)成為藉由前後之差壓而被動地進行開閉 之止回閥。 於上述ru缸1之上部設置有餘隙穴6，餘隙穴6之容積構 成為可藉由餘隙穴之驅動部8而變更。 於上述汽缸1之上述各吸入閥12a、⑶側，形成有用以 吸入吸入氣體A之吸入口 13a，於各喷出閥⑷、⑽侧， 形成有用以喷出喷出氣體B之喷出口 13b。 100129157 201211392 於上述餘隙穴6之餘隙穴本體60之兩側，設置有一對安 裝凸緣部50，上述汽缸1之上側氣體壓縮室2a與餘隙穴本 體60之穴背壓室51之間，係藉由具有第1節流器52的第 1導壓配管55而連通。 又，上述吸入氣體A之吸入口 13a與上述穴背壓室51之 間，係藉由具有第2節流器54之第2導壓配管55A而連通。 圖2係圖1之餘隙穴6之詳細放大圖，於上述餘隙穴本體 60内，在上下方向滑動自如地設置有由滑環56及遊碼環57 所構成之餘隙活塞58。 設置於上述餘隙活塞58之桿59構成為：經由設置於上述 餘隙穴本體60上面之罩蓋70之密封件72a與密封固定蓋 72而向上方延伸設置，從而不使該穴背壓室51内之氣體向 餘隙穴本體60與罩蓋70外洩漏。 於上述桿59之上部形成有外螺紋59a，於該外螺紋59a 外周，設置有具有螺合於外螺紋59a之内螺紋73之螺母74。 上述螺母74由具有内螺紋73之作為上螺桿之第1螺母部 75、及具有内螺紋73之作為下螺桿之第2螺母部76所構 成，各螺母部75、76構成為：例如，以經由以盤彈簧等所 構成之彈簧構件77而向反方向施力之狀態稍微滑動。 上述各螺母部75、76構成為：由彈簣構件77產生之彈力 成為最佳，於成為外螺紋59a與内螺紋73間不存在反衝之 狀態之時間點，固定螺桿78自第2螺母部76之外側插入而201211392 乂. The second gear' is configured to move the rod and the clearance piston by the driving of the driving body, and the piston back pressure of the clearance piston is used to make the suction and pressure of the steam red The intermediate intermediate pressure acts as a configuration in which the piston back pressure of the clearance piston is used to cause the suction pressure of the cylinder to function, and the spring member is constituted by a disk magazine. (Effect of the Invention) The clearance hole of the reciprocating compressor of the present invention is configured as described above, so that the following effects can be obtained. In other words, the cylinder includes a piston in which a suction port and a discharge port are formed, and the upper side gas (four) chamber and the lower side body H are divided by the piston, and are disposed on the upper portion of the cylinder and The upper side gas waste chamber 2 is connected to each other and has a cavity chamber and a cavity chamber body of the cavity chamber, a clearance piston in the gap chamber, and a drive for sliding the clearance piston, and the clearance is The sliding of the piston causes the clearance of the back and forth actuating compressor with the variable volume of the upper side gas compression chamber = the chamber to be placed on the clearance piston and has an external thread and is screwed by the anti-rotation device The nut of the external thread and the third member that is formed by the spring member and urged in the opposite direction via the spring member, the first two pairs of materials, and the pre-variation, Therefore, even if the sound of the occlusal portion of the screw disappears and acts on the rod, it will not break due to the tapping of the screw surface. 100129157 201211392 Loss and the clearance piston advances and retreats by making the cylinder side The thread is rotated forward and reversed. Further, in the state where the clearance piston is stopped, the spring member a& even if the fluctuation is negative, the screw surface is always urged in the direction and the frictional force is increased, so that the clearance piston does not move arbitrarily. Further, a second gear having η placed on the outer circumference of the nut and a second record disposed on the driving body and engaged with the first wire, and the rod and the clearance piston are driven by the driving of the driving body The movement is performed by using the driving body to rotate the gear to advance and retreat the clearance piston, whereby the _ volume can be changed by remote operation. The capacity adjustment of the compressor can be automatically performed if the input signal is taken in accordance with the human right and the clearance piston is configured to advance and retreat as a necessary amount of gas. Further, the fluctuation load acting on the clearance piston is large in addition to the suction/discharge pressure of the compressor and the weight of the component, and the back pressure acting on the back pressure chamber of the clearance piston is greatly affected. In the case where the average pressure in the cylinder is applied to the pocket back pressure chamber, the inside of the cylinder and the pocket back pressure chamber are connected via a restrictor such as an orifice. However, in this case, the same effect can be obtained by the fact that β is placed in contact with the pores of the back pressure chamber of the front face of the clearance piston, so that the construction becomes simple. On the other hand, since the amplitude of the load acting on the clearance piston largely changes in the vertical direction, it is necessary to increase the elastic force acting between the nuts. In addition, there is a disadvantage that the torque required to rotate the nut is also increased in order to move the clearance piston. In the case where the suction pressure is applied to the back pressure chamber, the amplitude 100129157 201211392 as the load is also equal to the above. However, the weight due to the weight is relatively higher than the pressure load. The weight is small. Therefore, the elastic force acting by the spring member is small, and the torque required to rotate the nut can be reduced. [Embodiment] [Embodiment] Hereinafter, a preferred embodiment of the clearance hole of the reciprocating compressor of the present invention will be described with reference to FIG. In addition, the same or equivalent parts as those in Fig. 3 are denoted by the same reference numerals. In Fig. 1, a cylinder bore is provided on the frame 1A of the compressor, and the piston 2 driven via the piston rod 2c is moved back and forth in the cylinder bore. The cylinder is a double-acting type that compresses the gas on the upper surface and the lower side of the piston 2, and the suction valve 12a, 12b and the discharge valve 14a are respectively disposed in the upper gas compression chamber 2a and the lower gas compression chamber 沘. , 14b. These cylinder valves (suction valves 12a and 12b and discharge valves 14a and 14b) are check valves that are passively opened and closed by differential pressures before and after. A clearance hole 6 is provided in the upper portion of the ru cylinder 1, and the volume of the clearance hole 6 is configured to be changed by the drive portion 8 of the clearance hole. On the side of each of the suction valves 12a and (3) of the cylinder 1, a suction port 13a for sucking in the suction gas A is formed, and on the sides of the discharge valves (4) and (10), a discharge port 13b for discharging the discharge gas B is formed. 100129157 201211392 A pair of mounting flange portions 50 are disposed on both sides of the clearance hole body 60 of the clearance hole 6, and between the gas compression chamber 2a on the upper side of the cylinder 1 and the pocket back pressure chamber 51 of the clearance hole body 60 The first pressure guiding pipe 55 having the first throttle 52 is connected to each other. Further, the suction port 13a of the suction gas A and the hole back pressure chamber 51 communicate with each other via the second pressure guiding pipe 55A having the second restrictor 54. Fig. 2 is a detailed enlarged view of the clearance hole 6 of Fig. 1. In the clearance hole body 60, a clearance piston 58 composed of a slip ring 56 and a code ring 57 is slidably provided in the vertical direction. The rod 59 provided on the clearance piston 58 is configured to extend upward through the seal 72a of the cover 70 provided on the upper surface of the clearance hole body 60, and the seal fixing cover 72 so as not to make the pocket back pressure chamber The gas in 51 leaks to the outside of the clearance pocket body 60 and the cover 70. An external thread 59a is formed on the upper portion of the rod 59, and a nut 74 having an internal thread 73 screwed to the external thread 59a is provided on the outer circumference of the external thread 59a. The nut 74 is composed of a first nut portion 75 having an internal screw 73 as an upper screw and a second nut portion 76 as a lower screw having an internal thread 73. Each of the nut portions 75 and 76 is configured, for example, via The spring member 77 composed of a disk spring or the like is slightly slid in a state of being biased in the opposite direction. Each of the nut portions 75 and 76 is configured such that the elastic force generated by the magazine member 77 is optimal, and the fixing screw 78 is from the second nut portion at a time when there is no backlash between the external thread 59a and the internal thread 73. Inserted on the outside of 76
100129157 10 S 201211392 固定各螺母部75、76之位置關係。 於上述罩蓋70上，由複數個棒狀體等所構成之支 大態:設置’設置於上述桿59之防轉器84之端部 •⑽構成為：相對於上述切部79而上下作動自 引，從而上述桿59僅y τ A 作動自如地被導100129157 10 S 201211392 Fixes the positional relationship between the nut portions 75 and 76. The cover 70 is formed by a plurality of rod-shaped bodies or the like: an end portion (10) provided with the anti-rotation device 84 provided on the rod 59 is configured to move up and down with respect to the cut portion 79. Self-referencing, so that the above rod 59 is only y τ A freely guided
上下作動而不進行旋及負之負重方向DActing up and down without rotating and negative load direction D
械!=部79之上部固定有台狀之機械台90,於該機 械口 90 ’經由一對軸承91 A 於該螺母74<_上述第如地保持有上述螺母％， 固定而設置有P齒輪93 a之外周，經由密矯92 於上述機械台9〇之上Λ 驅動體94 -I 。’ 5又置有由氣動馬達等所構成之 ^ 驅動體94之旋轉軸％之第2齒輪96 係與上述第1齒輪93咬合。 之第2齒輪96 因此，構成為：藉由啦在Λ %而螺母Μ進㈣轉Τ 94之媒動，經由各齿輪93、 切換媒動體94之空此餘隙活塞58上下作動，並且 74之正轉.反轉。因此〜端口（未叫，藉此可實現螺母 述外螺紋59a、螺母74 舰穴之艇動部8係由上 部79及驅動體94等構成各齒輪93、96、機械台9〇、支樓 八 動作進行敍述。於如上所述般對驅動94、隹- 驅動，並經由各齒輪93、96使螺母化動體94進订 構成螺母74之各物7 6使螺母74㈣之情況下，用以 累母4乃、76經由彈簧構件77相互向反 100129157 11 201211392 方向施力’故預先對内螺紋73施加負重(預負重），從而因 施加於上述餘隙活塞58之氣屢與上述預負重，而為了使螺 母％旋轉需要相對較大之轉矩，但第〗齒輪％之直徑較第 2齒輪96之直徑大η倍，藉此，藉由大減速比之大轉矩而 螺母74容易地旋轉’藉由無反衝之外螺紋地與内螺紋乃 之咬合旋轉而使餘隙活塞58高精度地上下作動，從而可使 氣體壓調整用穴室31之容積可變。 於上述情況下，在使餘隙活塞58移動時，穴背壓室51 之容積改變而氣體_•膨脹。作為用以避免該情形之一個 方法，如圖i所示，將汽虹！與穴f _ 51經由且有第工 節流器52之第i導壓配管55連接。又，汽虹ι内之壓力伴 隨活塞2之上下作動而於吸人與喷出壓之間變動，作由於呈 有^節流器52,故藉由該上下作動而產生之氣體向穴:者 壓室51之進出較少’結果穴背壓室51保持為吸人壓力與喷 出壓力之平均壓力。於該情況下，對於餘隙活塞58，以i 週期為單位而吸人/喷出壓力差之1/2之堡力於正負方向 上交替地作用。（實際施加之負重狀態係藉由桿59之 剖面積分之受壓面積的差及餘隙活塞58或桿％之重量而略 微改變。） 又，作為其他方法，如圖i所示，將汽紅i之吸入氣體A 之吸入口 13a或吸入閥冑12A與穴賴室51，經由具有第 2節流器54之第2導壓配管55A連接。上述吸入口 Ba或 100129157A machine-shaped mechanical table 90 is fixed to the upper portion of the mechanical part ==, and the mechanical port 90' is fixed to the nut 74 by a pair of bearings 91 A. The above-mentioned nut % is held in the above-mentioned portion, and the P gear is fixed. On the outer circumference of 93 a, the driving body 94 -I is mounted on the above mechanical table 9 through the dense correction 92 . Further, a second gear 96 having a rotational axis % of the driving body 94 formed of a pneumatic motor or the like is engaged with the first gear 93. Therefore, the second gear 96 is configured such that the nut is moved to the fourth (four) switch 94 by the nut, and the clearance piston 58 is moved up and down via the gears 93 and the switching medium 94, and 74 Positive turn. Reverse. Therefore, the port is not called, so that the nut-moving portion 8 of the nut and the nut 74 of the nut 74 can be realized by the upper portion 79 and the driving body 94, and the gears 93, 96, the mechanical table 9, and the branch eight. The operation is described. The drive 94 and the 隹-drive are performed as described above, and the nut runners 94 are stapled via the gears 93 and 96 to form the nut 74. The nut 74 is used to make the nut 74 (four) The females 4 and 76 are biased toward each other by the spring member 77 in the direction of the opposite direction 100129157 11 201211392. Therefore, a load (preload) is applied to the internal thread 73 in advance, so that the air applied to the clearance piston 58 repeatedly overlaps with the above-mentioned preload. In order to rotate the nut %, a relatively large torque is required, but the diameter of the first gear % is η times larger than the diameter of the second gear 96, whereby the nut 74 is easily rotated by the large reduction ratio of the large torque. The clearance of the gas pressure adjusting chamber 31 can be made variable by the high-precision movement of the clearance piston 58 by the rotation of the internal thread without the backlash and the rotation of the internal thread. In the above case, When the clearance piston 58 moves, the volume of the pocket back pressure chamber 51 As a method for avoiding this, as shown in Fig. i, the steam rainbow is connected to the hole f_51 via the ith pressure guiding pipe 55 of the second throttle device 52. Moreover, the pressure in the steam rainbow ι varies between the suction and the discharge pressure accompanying the upper and lower movements of the piston 2, and since the throttle device 52 is provided, the gas generated by the up and down movement is directed to the hole: The pressure chamber 51 has less entry and exit. The result is that the back pressure chamber 51 maintains the average pressure of the suction pressure and the discharge pressure. In this case, for the clearance piston 58, the suction/ejection pressure is in units of i cycles. The difference of 1/2 of the force acts alternately in the positive and negative directions. (The actual applied load-bearing state is slightly changed by the difference in the pressure-receiving area of the cross-section integral of the rod 59 and the weight of the clearance piston 58 or the rod %. Further, as another method, as shown in FIG. 1, the suction port 13a of the suction gas A of the steam red i or the suction valve port 12A and the hole chamber 51 are passed through the second pressure guiding pipe having the second throttle 54 55A connection. The above suction port Ba or 100129157
12 S 201211392 吸入閥室12A亦藉由向汽缸1内之間斷性之吸入動作而存 在壓力變動，因此，較理想的是於第2導壓配管55A之中 途裝入第2節流器54。於該情況下，大致吸入/噴出壓力差 分之負重僅於正方向C間斷地作用於餘隙活塞58。 本發明並不限定於上述實施形態，可適當自如地變形、改 良等。除此之外，只要為可達成本發明者，則上述實施形態 之各構成要素之材質、形狀、尺寸、數值、形態、數量、配 置部位等為任意且並無限定。 詳細地、又參照特定之實施態樣對本發明進行了說明，但 業者應當瞭解，可於不脫離本發明之精神與範圍内進行各種 變更及修正。 本申請案係基於2010年8月17日申請之日本專利申請 (曰本專利特願2010-182245)者，其内容於此處作為參照併 入本文。 (產業上之可利用性） 本發明之來回作動壓縮機之餘隙穴係例如可藉由遠距離 操作而簡單地進行化學設備等之氣體壓縮等容量可變動作。 【圖式簡單說明】 圖1係表示本發明之來回作動壓縮機之餘隙穴之概略構 成圖。 圖2係表示圖1之餘隙穴之具體構成之放大剖面圖。 圖3係表示先前之來回作動壓縮機之構成圖。 100129157 13 201211392 圖4係表示先前之來回作動壓縮機之主要部分之剖面圖。 【主要元件符號說明】 1 汽缸 1A 框架 2 活塞 2a 上側氣體壓縮室 2b 下側氣體壓縮室 2c 活塞棒 A 吸入氣體 B 喷出氣體 C 正之負重方向 D 負之負重方向 3 、 6 ' 41a 餘隙穴 4 第1活塞體 5 第1連結棒 7 活塞體 8 餘隙穴之驅動部 11 油壓手段 12a ' 12b 吸入閥 12A 吸入閥室 13a 吸入口 13b 喷出口 100129157 1412 S 201211392 Since the suction valve chamber 12A also has a pressure fluctuation due to the intermittent suction operation in the cylinder 1, it is preferable to insert the second throttle 54 into the second pressure guiding pipe 55A. In this case, the load of the substantially suction/discharge pressure difference acts on the clearance piston 58 intermittently only in the positive direction C. The present invention is not limited to the above embodiment, and can be appropriately modified or improved. In addition, the material, the shape, the size, the numerical value, the form, the number, the arrangement portion, and the like of the respective constituent elements of the above-described embodiments are arbitrary and not limited as long as they are inventors. The present invention has been described in detail with reference to the specific embodiments thereof. It is understood that various changes and modifications may be made without departing from the spirit and scope of the invention. The present application is based on Japanese Patent Application No. 2010-182245, filed on Jan. (Industrial Applicability) The clearance hole of the reciprocating compressor of the present invention can be easily subjected to a variable capacity operation such as gas compression of a chemical device or the like by remote operation. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing a schematic configuration of a clearance hole of a reciprocating compressor of the present invention. Fig. 2 is an enlarged cross-sectional view showing the specific configuration of the clearance hole of Fig. 1. Fig. 3 is a view showing the construction of a conventional back and forth actuating compressor. 100129157 13 201211392 Figure 4 is a cross-sectional view showing the main part of the previous reciprocating compressor. [Main component symbol description] 1 Cylinder 1A Frame 2 Piston 2a Upper gas compression chamber 2b Lower gas compression chamber 2c Piston rod A Intake gas B Ejected gas C Positive load direction D Negative load direction 3, 6 ' 41a Clearance 4 First piston body 5 First connecting rod 7 Piston body 8 Driving portion of clearance hole 11 Hydraulic means 12a ' 12b Suction valve 12A Suction valve chamber 13a Suction port 13b Ejection port 100129157 14
S 201211392 14a、14b 喷出閥 31 穴室 40 汽缸 40h 氣體壓縮室 41 汽缸罩蓋 41b 隔離壁 41c 氣體通過孔 42 外蓋 43 間隙調整桿 43s 螺桿桿部 43t 錐形桿部 44 桿支持模具 45 步進馬達 50 安裝凸緣部 51 穴背壓室 52 第1節流器 54 第2節流器 55 第1導壓配管 55A 第2導壓配管 56 滑環 57 遊碼環 58 餘隙活塞 100129157 15 201211392 59 桿 59a 外螺紋 60 餘隙穴本體 61 平衡室 62 連通路徑 70 罩蓋 71 0型環 72 密封固定蓋 72a 密封件 73 内螺紋 74 螺母 75 第1螺母部（上螺桿) 76 第2螺母部（下螺桿) 77 彈簧構件(盤彈簧） 78 固定螺桿 79 支撐部 84 防轉器 84a 端部 90 機械台 91 軸承 92 密鑰 93 第1齒輪 100129157 16 201211392 94 95 96 驅動體 旋轉軸 第2齒輪 100129157S 201211392 14a, 14b Discharge valve 31 Chamber 40 Cylinder 40h Gas compression chamber 41 Cylinder cover 41b Partition wall 41c Gas passage hole 42 Cover 43 Gap adjustment rod 43s Screw rod portion 43t Conical rod portion 44 Rod support mold 45 steps Feed motor 50 Mounting flange portion 51 Hole back pressure chamber 52 First throttle 54 Second throttle 55 First pressure regulating pipe 55A Second pressure guiding pipe 56 Slip ring 57 Travel ring 58 Clearance piston 100129157 15 201211392 59 rod 59a external thread 60 clearance hole body 61 balance chamber 62 communication path 70 cover 71 0 type ring 72 seal fixing cover 72a seal 73 internal thread 74 nut 75 first nut portion (upper screw) 76 second nut portion ( Lower screw) 77 Spring member (disk spring) 78 Fixing screw 79 Support portion 84 Anti-rotation device 84a End 90 Mechanical table 91 Bearing 92 Key 93 First gear 100129157 16 201211392 94 95 96 Drive body rotation shaft 2nd gear 100129157