HUE035664T2 - Reciprocating compressor - Google Patents

Abstract

A reciprocating compressor according to at least one embodiment of the present invention includes a housing which includes an intake chamber, a discharge chamber, a cylinder, and a crank chamber, the crank chamber having a lower portion formed as an oil storage chamber configured to store lubricant; a piston which is reciprocatively located in the cylinder; a crank shaft which is rotatably arranged in the crank chamber and is coupled to the piston via a connecting rod; a pressure equalization path through which the intake chamber and the crank chamber communicates, the pressure equalization path having an opening end open to the crank chamber; and a partition member which is located between the crank shaft and the opening end of the pressure equalization path. The partition member extends below the crank shaft from one side of the crank shaft to the other side of the crank shaft so as to cover at least the lower side of the crank shaft.

Description

Description ent Document 1 includes a pump. In the reciprocating compressor under operation, the lubricant in the oil stor- TECHNICAL FIELD age chamber is sucked up by the pump to be supplied to the bearing, which supports the crank shaft, and the [0001] The present application relates to a reciprocat- 5 like through an oil path disposed in the housing and the ing compressor. crank shaft.

Another reciprocating compressor is disclosed in docu-BACKGROUND ment US 2 008 715 A.

[0002] A reciprocating compressor is applied to, for ex- 10 Citation List ample, a refrigeration cycle and is used for compressing a coolant. Patent Literature [0003] For example, as described in Patent Document 1, an intake chamber, a discharge chamber, a cylinder, [0009] Patent Document 1: US Patent No. 4,887,514 and a crank chamber are defined in a housing of the 15 (Specification) reciprocating compressor. A lower portion of the crack

chamber is used as an oil storage chamber configured SUMMARY to store lubricant. A piston is reciprocatively located in the cylinder. A crank shaft is rotatably arranged in the Technical Problem crank chamber via a bearing. The piston is coupled to 20 the crank shaft via a connecting rod. Thus, rotational [0010] In the reciprocating compressor disclosed in movement of the crank shaft is converted into the recip- Patent Document 1 under operation, the pressure differ- rocating movement of the piston. ence between the crank chamberand the intake chamber [0004] The cylinder can communicate with the intake causes the leakgas in the crank chamberto return to the chamber and the discharge chamber via an intake valve 25 intake chamber through the pressure equalization path, and a discharge valve, respectively. When power is sup- In particular, when the reciprocating compressor transi- plied to the crank shaft from the outside and thus the tions from the no load operation to the normal operation piston makes the reciprocating movement in the recip- due to the load change, the pressure in the intake cham- rocating compressor under operation, gas as the com- bersharply drops. Thus, the pressure difference between pression target is sucked into the cylinderfrom the intake 30 the crank chamber and the intake chamber increases, chamber via the intake valve, compressed, and then is As a result, the flow speed (returning speed) of the leak discharged into the discharge chamber via the discharge gas returning to the intake chamberthrough the pressure valve. equalization path increases.

[0005] While the gas is being compressed in the cyl- [0011] In the reciprocating compressor under opera- inder, the gas as the compression target (leakgas) leaks 35 tion, the lubricant which has lubricated the bearings spat-through a gap between an inner circumference surface ters in the form of droplets in the crank chamber. The of the cylinder and a piston ring, to flow into the crank spattered droplets of the lubricant flow into the intake chamber. To prevent the pressure in the crank chamber chamberthrough the pressure equalization path, togeth-from rising due to the leak gas, a pressure equalization er with the flowing leak gas. The lubricant stored in the path, through which the crank chamber and the intake 40 intake chamber is sucked into the cylinder and then is chamber communicate, is provided. discharged. The amount of the lubricant which flows into [0006] Thus, when the compressor is under a normal the intake chamber increases with the returning speed operation (load operation), the leak gas in the crank of the leak gas. Thus, when the return speed is high, the chamber is returned to the intake chamberthrough the amountofthelubricantdischarged from the reciprocating pressure equalization path. The reciprocating compres- 45 compressor is large, and as a result, the amount of the sor in Patent Document 1 includes an unload mecha- lubricantinthereciprocatingcompressorisreduced.This nism, and thus can operate in a state where the intake might eventually lead to oil loss. valve is opened (no load operation). When the load op- [0012] In the reciprocating compressor disclosed in eration transitions to the no load operation, the pressure Patent Document 1, the pressure equalization pipe, in the intake chamberrises, and gasflowsfrom the intake so formed as the pressure equalization path, has a function chamber to the crank chamber through the pressure as an oil separator. When the returning speed of the leak equalization path. gas is high, the lubricant in the pressure equalization path [0007] In the reciprocating compressor in Patent Doc- is blown up by the leak gas. Thus, the amount of the ument 1, a pressure equalization pipe is formed outside lubricant discharged from the reciprocating compressor of the housing, as the pressure equalization path. Alter- 55 increases, and thus the amount of the lubricant in the natively, the pressure equalization path may be disposed reciprocating compressor is reduced, even in the recip- in the housing. rocating compressor having the oil separator in the pres- [0008] The reciprocating compressor disclosed in Pat- sure equalization path. This might eventually lead to oil loss. into the oil storage chamber through the gap between [0013] An object of at least one embodiment of the the partition plates. present invention is to provide a reciprocating compres- [0022] A reciprocating compressor according to one sor in which reduction of lubricant is prevented. embodiment further includes a collecting member which 5 is located between the gap between the partition plates Solution to Problem and collects the lubricant which passes through the gap.

[0023] In this configuration, the amount of the lubricant [0014] A reciprocating compressor according to at which flows into the opening end of the pressure equal-least one embodiment of the present invention includes ization path is further reduced, and thus the lubricant is a housing which includes an intake chamber, a discharge 10 further prevented from being discharged from the recip-chamber, a cylinder, and a crank chamber, the crank rocating compressor. chamber having a lower portion formed as an oil storage [0024] A reciprocating compressor according to one chamber configured to store lubricant; a piston which is embodimentfurther includes an oil separator located be- reciprocatively located in the cylinder; a crank shaft which tween the partition member and the opening end of the is rotatably arranged in the crank chamberand is coupled 15 pressure equalization path. The oil separator includes: a to the piston via a connecting rod; a pressure equalization labyrinth portion which is formed on a side closer to the path through which the intake chamber and the crank partition member and defines a winding flow path; and a chamber communicates, the pressure equalization path hollow portion which is formed on a side closer to the having an opening end open to the crank chamber; and opening end and defines a flow path having a larger a partition member which is located between the crank 20 cross-sectional area than the flow path defined by the shaft and the opening end of the pressure equalization labyrinth portion. path. The partition member extends below the crank shaft [0025] In this configuration, the diameter of oil droplets from one side of the crank shaft to the other side of the increases as the oil droplets pass through the labyrinth crank shaft so as to cover at least the lower side of the portion, and the separation of the oil droplets passing crank shaft. 25 through the hollow portion from gas is facilitated by grav- [0015] In this configuration, droplets of the lubricant itational settling. As a result, the oil droplets are efficiently scattering from the crank shaft collide on the partition collected by the oil separator. Thus, the amount of the member, and thus do not directly flow into the opening lubricantwhich flows into the opening end of the pressure end of the pressure equalization path. Thus, the amount equalization path is furtherreduced, whereby the amount of the lubricant which flows into the intake chamber 30 of the lubricant discharged from the reciprocating corn-through the pressure equalization path is reduced, and pressor is further reduced. thus the lubricant is prevented from being discharged from the reciprocating compressor. Advantageous Effects [0016] In a reciprocating compressor according to one embodiment, the partition member includes a plurality of 35 [0026] With at least one embodiment of the present partition plates, and the plurality of partition plates are invention, a reciprocating compressor in which reduction arranged along an axial direction of the crank shaft. of lubricant is prevented is provided.

[0017] In this configuration, the partition member in

cludes a plurality of partition plates, and thus can be eas- BRIEF DESCRIPTION OF DRAWINGS ily arranged in the crank chamber. 40 [0018] In a reciprocating compressor according to one [0027] embodiment, the partition plates each include: a lower portion which has a quarter cylinder shape and is curved [FIG. 1] FIG. 1 is a schematic vertical cross-sectional along a lower side of the crankshaft; and an upper portion view of a reciprocating compressor according to one which continues to the lower portion and is positioned on 45 embodimentofthe present invention, also illustrating a side closer to the crank shaft. the configuration of a refrigeration cycle.

[0019] In this configuration, droplets which have col- [FIG. 2] FIG. 2 is a schematic horizontal cross-sec- lided on the partition plates are collected in the lower tional view of the reciprocating compressor in FIG. 1. portion of the partition plates, and then smoothly flow into [FIG. 3] FIG. 3 is a perspective view schematically the oil storage chamber. so illustrating partition plates in FIGs. 1 and 2.

[0020] In a reciprocating compressor according to one [FIG. 4] FIG. 4 is a schematic horizontal cross-sec- embodiment, end portions of the plurality of partition tional view of a reciprocating compressor according plates which are adjacent to each other in the axial di- to another embodiment. rection of the crank shaft overlap one another in a thick- [FIG. 5] FIG. 5 is a partial schematic horizontal crossness direction of the partition plates with a gap in be- 55 sectional view of a reciprocating compressoraccord- tween. ing to another embodiment.

[0021] In this configuration, droplets collected in the [FIG. 6] FIG. 6 is a schematic outer view of an oil lower portion of each ofthe partition plates smoothly flow separator in FIG. 6.

[FIG. 7] FIG. 7 is a partial schematic horizontal cross- cylinder block. sectional view ofa reciprocating compressor accord- [0035] One end of the cylinder 32 communicates with ing to still another embodiment. the crank chamber 34. A connecting rod 38 connected [FIG. 8] FIG. 8 is a view illustrating a state in which to the piston 36 extends into the crank chamber 34. In a collecting member is disposed in the gap between 5 the crank chamber 34, a crank shaft 40 is rotatably dis- the partition plates in FIG. 3. posed and the connecting rod 38 is connected to the crank shaft 40. More specifically, the crank shaft 40 is DETAILED DESCRIPTION rotatably supported by the housing 22 via a plain bearing as a radial bearing. The plain bearing as the radial bear- [0028] Embodiments of the present invention are de- 10 ing is also located between the connecting rod 38 and scribed below with reference to the drawings. The sizes, the piston 36 and the crank shaft 40. materials, shapes, relative positions, and the like of the [0036] One end side of the crank shaft 40 is airtightly components described in the embodiments or illustrated disposed through the housing 22, and an unillustrated in the drawings are merely examples for the description driving source is connected to an outer end of the crank and there is no intension to limit the scope of the present 15 shaft 40. When the driving source rotates the crank shaft invention thereto. 40, the piston 36 reciprocates in the cylinder 32, whereby [0029] FIG. 1 is a schematic vertical cross-sectional intake, compressing, and discharging steps for the cool- view of a reciprocating compressor according to one em- ant are repeatedly executed. bodiment, and is also a schematic view illustrating the [0037] The reciprocating compressor according to the configuration of a refrigeration cycle employing the re- 20 present embodiment includes an unloader mechanism ciprocating compressor. (capacity control mechanism) configured to change a dis- [0030] The refrigeration cycle includes a circulation charge capacity in accordance with a load. More specif- path 10 in which a coolant circulates. ically, the unloader mechanism includes an unloader pis-

The circulation path 10 includes the reciprocating com- ton 37 capable of operating in accordance with a load, pressor, a condenser (high pressure side heat exchang- 25 and can control the opening/closing of an intake valve in er) 12, an expansion valve (expander) 14, and an evap- accordance with the position of the unloader piston 37. orator (low pressure side heat exchanger) 16, arranged [0038] More specifically, the intake valve is constantly in this order in a circulation direction of the coolant. In opened by a link member, operating together with the the present embodiment, an oil separator 18 and a liquid unloader piston 37, when the load is reduced, whereby receiver 20 are disposed on the circulation path 10. 30 an intake capacity is reduced.

[0031] In the refrigeration cycle, for example, the re- When the state where the intake capacity is reduced con- ciprocating compressor sucks a coolant at a pressure of tinues and a load side temperature rises, evaporation of 1 MPa to 3 MPa (intake pressure), compresses the cool- the coolant in the evaporator 16 is facilitated, whereby ant, and discharges the coolant at a pressure of 4 MPa the intake pressure rises. to 6 MPa (discharge pressure). The ranges of the intake 35 [0039] To increase the intake capacity to lower the inpressure and the discharge pressure are not limited to take pressure, the capacity control mechanism is oper- those described above. The coolant is, for example, am- ated to change the position of the unloader piston 37. monia or carbon dioxide. Thus, the intake valve is no longer constantly opened, [0032] The reciprocating compressor includes a hous- whereby the intake capacity increases to return to the ing 22 provided with an intake port 24 and a discharge 40 original level. port 26. The intake port 24 is connected to an outlet of [0040] In the reciprocating compressor under opera- the evaporator 16 through a pipe, and the discharge port tion, lubricant is supplied to sliding members such as the 26 is connected to an inlet to the oil separator 18 through radial bearings and the pistons 36. Thus, a bottom portion a pipe. of the crank chamber 34 is defined as an oil storage [0033] The housing 22 incorporates an intake chamber 45 chamber 35 for the lubricant. The reciprocating compres-28, a discharge chamber 30, a cylinder 32, and a crank sor includes an oil pump 42 which operates togetherwith chamber 34. A piston 36 is reciprocatively located in the the crank shaft 40. The lubricant sucked up from the oil cylinder 32. A compression chamber is defined by the storage chamber 35 by the oil pump 42 is supplied to the piston 36 in the cylinder 32. The intake chamber 28 and sliding members through an oil path disposed in or out the discharge chamber 30 communicate with the intake so of the housing 22. The oil path is, for example, formed port 24 and the discharge port 26, and can communicate also in the crank shaft 40 as illustrated with a dotted line with the compression chamber through an intake valve in FIG. 1. and a discharge valve, respectively. [0041] In the present embodiment, oil filters 46 and 48 [0034] The reciprocating compressor according to the for cleaning the lubricant are disposed in the oil storage present embodiment is a multicylinder reciprocating 55 chamber 35 and out of the housing 22, respectively, compressor including a plurality of pistons 36 and a plu- [0042] FIG. 2 is a schematic horizontal cross-sectional rality of cylinders 32. Each of the cylinders 32, defined view of the reciprocating compressor in FIG. 1. by a cylinder sleeve, may alternatively be defined by a [0043] In the reciprocating compressor under opera- tion, the coolant leaks through a gap between the piston scatterfrom thecrankshaft40and the bearings, the drop- 36 and a wall surface of the cylinder 32, and flows into lets collide on the partition plate 54, and thus do not di- the crank chamber 34. The reciprocating compressor in- rectly flow into the inlet end ofthe pressure equalization eludes a pressure equalization path 50 through which path 50. Thus, the amount of the lubricantwhich flows the intake chamber 28 and the crank chamber 34 com- 5 into the intake chamber 28 through the pressure equal-municate, to prevent the leaked coolant (leak gas) from ization path 50 is reduced, and thus the lubricant is preraising the pressure in the crank chamber 34. In the vented from being discharged from the reciprocating present embodiment, a through hole as the pressure compressor. equalization path 50 is formed in the housing 22. [0051] In conventional reciprocating compressors, [0044] The pressure equalization path 50 includes an 10 when the unloader mechanism operates to reduce the opening end (inlet end) open to the crank chamber 34 intake capacity and temporarily establish a no load op- and an opening end (outlet end) open to the intake cham- eration state, and then the intake capacity increases and ber 28. The inlet end of the pressure equalization path the state transitions to a normal operation state, the in- 50 is positioned above a normal oil surface level of the take pressure sharply drops. Thus, the droplets are likely lubricant in the oil storage chamber 35. 15 to flow into the pressure equalization path. In the recip- [0045] As shown in FIG. 1 and FIG. 2, the reciprocating rocating compressor according to the embodiment decompressor according to the present embodiment in- scribed above, the partition plate 54 prevents the droplets eludes a partition member 52 which partitions the crank from directly flowing into the inlet end of the pressure shaft 40 from the opening end of the pressure equaliza- equalization path 50 when the no load operation state tion path 50. In the present embodiment, the partition 20 transitions to the normal operation state. member 52 includes three partition plates 54a, 54b, and [0052] In the reciprocating compressor according to 54c. The partition plates 54a, 54b, and 54c are also col- the embodiment, the partition member 52 includes a plu- lectively referred to as a partition plate 54. rality of partition plates 54, and thus can be easily ar- [0046] As shown in FIG. 3, the partition plate 54 in- ranged in the crank chamber 34. eludes a lower portion 56 which has a substantially quar- 25 [0053] In the reciprocating compressor according to ter cylinder shape and upper portions 58 which continue the embodiment, the droplets which have collided on the to the lower portion 56 and have aflat plate shape. Upper partition plates 54 are collected in the lower portion 56 endsides of theupper portions 58 are fixed to the housing protruding downward, and then smoothly flow into the oil 22 with fixing members such as bolts. storage chamber 35 through the gap between the parti- 10047] When the partition plate 54 is fixed to the hous- 30 tion plates 54. ing 22, the lower portion 56 of the partition plate 54 is [0054] The present invention is not limited to the em- curved to protrude downward along the lower side ofthe bodiment described above, and includes embodiments crank shaft 40. The upper portions 58 are inclined to have obtained by modifying the embodiment described above, a portion farther from the crank shaft 40 in a horizontal as exemplarily described below. In the description ofthe direction positioned at a higher portion, and are posi- 35 embodiments below, the configurations which are the tioned on both sides of the crank shaft 40 in the horizontal same as or similar to the embodiment described above direction orthogonal to the crank shaft 40. are denoted with the same reference numerals and the [0048] In other words, the partition plate 54 extends description thereof will be omitted. from a portion ofthe housing 22 on one side ofthe crank [0055] FIG. 4 is a schematic horizontal cross-sectional shaft 40 to a portion ofthe housing 22 on another side 40 view of a reciprocating compressor according to another ofthe crank shaft 40 below a lower side ofthe crankshaft embodiment. 40 so as to cover at least the lower side ofthe crank shaft [0056] In the reciprocating compressor in FIG. 4, a 40. The lower portion 56 of the partition plate 54 has a pressure equalization pipe 60 is formed outside of the mostrecessed portion positioneddirectlybelowthecrank housing 22, as the pressure equalization path 50. shaft 40 . 45 [0057] Also in this configuration, the partition plate 54 [0049] The partition plate 54 extends along an axial prevents the droplets from directly flowing into the inlet direction ofthe crank shaft 40. The three partition plates end of the pressure equalization path 50. 54a, 54b, and 54c are arranged along the axial direction [0058] FIG. 5 is a partial schematic horizontal cross- of the crank shaft 40 with end portions of the partition sectional view of a reciprocating compressor according plates 54a, 54b, and 54c adjacent to each other overlap- so to still another embodiment. ping one another in a thickness direction ofthe partition [0059] The reciprocating compressor in FIG. 5 further plates 54a, 54b, and 54c with a gap in between. includes an oil separator 64 arranged in the crank cham- [0050] In the reciprocating compressor according to ber 34. the embodiment described above, the partition plate 54 [0060] FIG. 6 is a schematic outer perspective view of partitions the crank shaft 40 from the inlet end of the 55 the oil separator 64. As shown in FIG. 5 and FIG. 6, the pressure equalization path 50. Thus, in the reciprocating oil separator 64 includes a labyrinth portion 66 on a side compressor under operation, even when droplets ofthe closer to the partition plate 54 and a hollow portion 68 on lubricant, which has lubricated the bearings and the like, a side closer to the inlet end ofthe pressure equalization path. that the oil return path 82 is constantly closed by the [0061] The labyrinth portion 66 defines a winding flow lubricant. Thus, the oil droplets in the crank chamber 34 path, and the hollow portion 68 defines a flow path having do not directly flow into the oil return path 82 to reach the a larger cross-sectional area than that of the flow path intake chamber 28. defined by the labyrinth portion 66. 5 [0069] FIG. 8 exemplarily illustrates a configuration in [0062] More specifically, the oil separator 64 includes which a collecting member 84 is disposed in the gap be-a circumference wall 70 forming a cylinder shape and a tween the end portions of the partition plates 54. The flange 72 extending outward from one end of the circum- collecting member 84 has a mesh structure. The droplets ference wall 70. The axial direction of the circumference passing through the collecting member 84 are collected wall 70 is arranged towards the crank shaft 40. A plurality 10 to be large and the resultant large droplet flows down in of partition walls 76, each being orthogonal to the circum- the oil storage chamber. ference wall 70, are disposed on the inner side of the [0070] With the collecting member 84, the amount of circumference wall 70. The partition walls 76 are sepa- the lubricant flowing into the inlet end of the pressure rated from each other in an axial direction of the circum- equalization path 50 is further reduced, whereby the ference wall 70, and define the winding flow path in the 15 amountofthelubricantdischarged from the reciprocating labyrinth portion 66. The flange 72 is provided with a compressor is further reduced. through hole (gas return aperture 78) which communi- [0071] The oil separator 18, located between the re- cates with the inlet end of the pressure equalization path ciprocating compressor and the condenser 12 in the re- 50. frigeration cycle described above, may be omitted be- [0063] In the present embodiment, a through hole (oil 20 cause the amount of the lubricant discharged from the dropping aperture 80), through which an intermediate reciprocating compressor is reduced. portion of the pressure equalization path 50 and the crank [0072] The numberof partition plates 54, which is three chamber 34 communicate, is provided. The lubricant, in the partition member 52 described above, is not par- which has flowed down from the intake chamber 28, re- ticularly limited. The plate member, as the component of turns to the crank chamber 34 through the oil dropping 25 the partition plate 54, may be provided with a slit. Fur-aperture 80. The cross-sectional area of the oil dropping thermore, the partition plate 54 may be formed by a mesh aperture 80 is set in such a manner that the lubricant or punching metal member, and the like. stays on the oil dropping aperture 80. Thus, the oil drop lets in the crank chamber 34 does not directly flow into Reference Signs List the oil dropping aperture 80 to reach the intake chamber 30 28. [0073] [0064] A check valve which prevents a fluid from flow ing into the intake chamber 28 from the crank chamber 22 housing 34 may be disposed at the position of the oil dropping 28 intake chamber aperture 80. 35 30 discharge chamber [0065] In the reciprocating compressor, the diameter 32 cylinder of the oil droplets increases as the oil droplets pass 34 crank chamber through the labyrinth portion 66 of the oil separator 64, 35 oil storage chamber and the separation of the oil droplets passing through the 36 piston hollow portion 68 from gas is facilitated by gravitational 40 38 connecting rod settling. As a result, the oil droplets are efficiently collect- 40 crank shaft ed by the oil separator 64. Thus, the amount of the lubri- 50 pressure equalization path cant which flows into the inlet end of the pressure equal- 52 partition member ization path 50 is further reduced, whereby the amount 54 (54a, 54b, 54c) partition plate of the lubricant discharged from the reciprocating com- 45 56 lower portion pressor is further reduced. 58 upper portion [0066] In the reciprocating compressor, the upper por- 64 oil separator tions 58 of the partition plate 54 are inclined. Thus, the 66 labyrinth portion oil separator 64 can be arranged in the crank chamber 68 hollow portion 34 without preparing the housing 22 of a large size. so [0067] FIG. 7 is a partial schematic horizontal cross- sectional view of a reciprocating compressor according Claims to yet still another embodiment.

[0068] In the reciprocating compressor, an oil return 1. A reciprocating compressor comprising: path 82, through which the intake chamber 28 and the 55 crank chamber 34 communicate, is provided separately a housing (22) which includes an intake cham- from the pressure equalization path 50. The cross-sec- ber (28), a discharge chamber, a cylinder (32), tional area of the oil return path 82 is set in such a manner and a crank chamber (34), the crank chamber (34) having a lower portion (56) formed as an oil a labyrinth portion (66) which is formed on aside storage chamber (35) configured to store lubri- of the partition member (52) and defines a cant; curved flow path; and a piston (36) which is reciprocatively located in a hollow portion (68) which is formed on a side the cylinder (32); 5 of the opening end and defines a flow path hav- a crank shaft (40) which is rotatably arranged in ing a larger cross-sectional area than the flow the crank chamber (34) and is coupled to the path defined by the labyrinth portion (66). piston (36) via a connecting rod (38); a pressure equalization path (50) through which the intake chamber (28) and the crank chamber 10 Patentansprüche (34) communicate, the pressure equalization path (50) having an opening end open to the 1. Kolbenverdichter, umfassend: crank chamber (34); and a partition member (52) which is located be- ein Gehäuse (22), das eine Einlasskammer tween the crank shaft (40) and the opening end 15 (28), eine Auslasskammer, einen Zylinder (32) ofthe pressure equalization path (50), wherein und eine Kurbelkammer (34) enthält, wobei die the partition member (52) extends below the Kurbelkammer (34) einen unteren Abschnitt crankshaft (40) from one side ofthe crank shaft (56) aufweist, der als Ölvorratskammer (35) ge- (40) to the other side of the crank shaft (40) so bildet wird, konfiguriert, um Schmiermittelzu beás to cover at least the lower side of the crank 20 vorraten; shaft (40); and wherein the opening end is po- einen Kolben (36), der sich hin- und herbeweg- sitioned above a normal oil surface level ofthe lieh in dem Zylinder (32) befindet; lubricant in the oil storage chamber (35). eine Kurbelwelle (40), die drehbar in der Kurbel kammer (34) angeordnet ist und über eine Pleu- 2. The reciprocating compressor according to claim 1, 25 elstange (38) mit dem Kolben (36) verbunden wherein ist; the partition member (52) includes a plurality of par- ein Druckausgleichspfad (50), durch den die tition plates (54), and Einlasskammer(28)unddieKurbelkammer(34) the plurality of partition plates (54) are arranged verbunden sind, wobei der Druckausgleichs- along an axial direction of the crank shaft (40). 30 pfad (50) ein zu der Kurbelkammer (34) offenes Öffnungsende aufweist; und 3. The reciprocating compressor according to claim 2, ein Unterteilungselement (52) das sich zwi- wherein the partition plates (54) each include: a low- sehen der Kurbelwelle (40) und dem Öffnungs- er portion (56) which has a quarter cylinder (32) ende des Druckausgleichspfads (50) befindet, shape and is curved along a lower side of the crank 35 wobei shaft(40); and an upperportion (58)which continues sich das Unterteilungselement (52) unter der to the lower portion (56) and is positioned on a side Kurbelwelle (40), von einer Seite der Kurbelwel- of the crank shaft (40). le (40) zu der anderen Seite der Kurbelwelle (40) erstreckt, um zumindest die Unterseite der Kur- 4. The reciprocating compressor according to claim 3, 40 belwelle (40) abzudecken; wherein end portions of the plurality of partition und wobei das Öffnungsende über einem nor- plates (54) which are adjacent to each other in the malen Ölfüllstand des Schmiermittels in der Ölaxial direction of the crank shaft (40) overlap one Vorratskammer (35) positioniert ist. another in a thickness direction ofthe partition plates (54) with a gap in between. 45 2. Kolbenverdichter nach Anspruch 1, wobei das Unterteilungselement (52) eine Vielzahl von Un- 5. The reciprocating compressor according to claim 4, terteilungsplatten (54) enthält, und die Vielzahl von further comprising a collecting member which is Io- Unterteilungsplatten (54) entlang einer axialen Rich- cated between the gap between the partition plates tung der Kurbelwelle (40) angeordnet sind. (54) and collects the lubricantwhich passes through so the gap. 3. Kolbenverdichternach Anspruch 2, wobei die Unter teilungsplatten (54) jeweils enthalten: einen unteren 6. The reciprocating compressor according to claim 1, Abschnitt (56), der eine Viertelzylinder-Form (32) further comprising an oil separator (64) located be- aufweist und entlang einer Unterseite der Kurbelwel- tween the partition member (52) and the opening 55 |e (40) gekrümmt ist; und einen oberen Abschnitt end ofthe pressure equalization path (50), wherein (58),dersich bis zum unteren Abschnitt (56) fortsetzt the oil Separator (64) includes: und auf einer Seite der Kurbelwelle (40) positioniert ist. 4. Kolbenverdichter nach Anspruch 3, wobei En- l’organe de séparation (52) s’étend en dessous dabschnitte der Vielzahl von Unterteilungsplatten de l’arbre à vilebrequin (40) à partir d’un côté de (54), die in die axiale Richtung der Kurbelwelle (40) l’arbre à vilebrequin (40) jusqu’à l’autre côté de aneinander angrenzend sind, einander in der Di- l’arbre à vilebrequin (40), de façon à recouvrir ckenrichtung derUnterteilungsplatten (54) miteinem 5 au moins le côté inférieurde l’arbre à vilebrequin

Spalt dazwischen überschneiden. (40) ; et dans lequel l’extrémité d’ouverture est posi- 5. Kolbenverdichter nach Anspruch 4, weiter ein Sam- tionnée au-dessus d’un niveau de surface d’hui- melelement umfassend, das sich zwischen dem le normal du lubrifiant dans la chambre de stoc-

Spalt zwischen den Unterteilungsplatten (54) befin- 10 kage d’huile (35). det und das Schmiermittel aufsammelt, das den

Spalt durchquert. 2. Compresseur alternatif selon la revendication 1, dans lequel 6. Kolbenverdichter nach Anspruch 1, weiter einen Öl- l’organe de séparation (52) comporte une pluralité abscheider (64) umfassend, der sich zwischen dem 15 de plaques de séparation (54), et

Unterteilungselement (52) und dem Öffnungsende la pluralité de plaques de séparation (54) est agen- des Druckausgleichspfads (50) befindet, wobei cée le long d’une direction axiale de l’arbre à vile- der Ölabscheider (64) enthält: brequin (40). einen Labyrinth-Abschnitt (66), der auf einer 20 3. Compresseur alternatif selon la revendication 2,

Seite des Unterteilungselements (52) gebildet dans lequel les plaques de séparation (54) compor- wird, und einen gekrümmten Strömungspfad tent chacune : une portion inférieure (56) qui a une definiert; und forme de quart de cylindre (32) et est incurvée le einen hohlen Abschnitt (68), der auf einer Seite long d’un côté inférieurde l’arbre à vilebrequin (40) ; des Öffnungsendes gebildet wird und einen 25 et une portion supérieure (58) qui continue vers la

Strömungspfad definiert, der einen größeren portion inférieure (56) et est positionnée sur un côté

Querschnittsbereich aufweist, als der Strö- de l’arbre à vilebrequin (40). mungspfad, der durch den Labyrinth-Abschnitt (66) definiert wird. 4. Compresseur alternatif selon la revendication 3, 30 dans lequel des portions d’extrémité de la pluralité de plaques de séparation (54) qui sont adjacentes

Revendications les unes aux autres dans la direction axiale de l’arbre à vilebrequin (40) se chevauchent les unes les autres 1. Compresseur alternatif comprenant : dans une direction d’épaisseur des plaques de sé- 35 paration (54) avec un espace entre elles. un carter (22) qui comporte une chambre d’admission (28), une chambre d’évacuation, un cy- 5. Compresseur alternatif selon la revendication 4, lindre (32), et une chambre de vilebrequin (34), comprenant en outre un organe de collecte qui est la chambre de vilebrequin (34) ayant une portion situé entre l’espace entre les plaques de séparation inférieure (56) formant une chambre de stocka- 40 (54) et collecte le lubrifiant qui traverse l’espace, ge d’huile (35) configurée pour stocker un lubrifiant; 6. Compresseur alternatif selon la revendication 1, un piston (36) qui est situé dans le cylindre (32) comprenant en outre un séparateurd’huile (64) situé de sorte à être en mouvement alternatif; entre l’organe de séparation (52) et l’extrémité un arbre à vilebrequin (40) qui est agencé de 45 d’ouverture du chemin d’équilibrage de pression manière rotative dans la chambre de vilebrequin (50), dans lequel (34) et est couplé au piston (36) par l’intermé- le séparateurd’huile (64) comporte : diaire d’une bielle (38) ; un chemin d’équilibrage de pression (50) par l’in- une portion en labyrinthe (66) qui est formée sur termédiaire duquel communiquent la chambre 50 un côté de l’organe de séparation (52) et définit d’admission (28) et la chambre de vilebrequin un chemin d’écoulement incurvé ; et (34), le chemin d’équilibrage de pression (50) une portion creuse (68) qui est formée sur un ayant une extrémité d’ouverture ouverte dans la côté de l’extrémité d’ouverture et définit un che- chambre de vilebrequin (34) ; et min d’écoulement ayant une aire en coupe un organe de séparation (52) qui est situé entre 55 transversale plus grande que le chemin d’écou- l’arbre à vilebrequin (40) et l’extrémité d’ouver- lement défini par la portion en labyrinthe (66). ture du chemin d’équilibrage de pression (50), dans lequel

REFERENCES CITED IN THE DESCRIPTION

This list of references cited by the applicant is for the reader’s convenience only. It does not form part of the European patent document. Even though great care has been taken in compiling the references, errors or omissions cannot be excluded and the EPO disclaims all liability in this regard.

Patent documents cited in the description • US 2008715 A [0008] · US 4887514 A [0009]

Claims (6)

SZAB A DALMI IGÉNY ΡΟΝΤΟ K DUGΑ'ΠΎ OS KOMPRESSZOR 1 Dugattyús kmupn-rxíoí. amd\ fartahnaz. egy ha 'ai »22\ enx'K magúba fogkn eg) bemeneti kannal (?$' egs k-putogo \„n nt egy hengert (32} és egy (órg&amp;ííyúknmrtó (34 g amely forgattyúkamtának (34) van egy kenőanyag tárolására olajtároló kamraként (35) .kialakított alsó része (56); egy dugattyút (36), amely ki-be mozgathatóim a hengerben (32) van elhelyezve; egy iörgahyüréd (40) amely a teigatGukamíában (34) forgathatóaa van elrendezve, és egy csatiaké o a adón (33) keresztül a dugattyúval 06) van Össze kapcsolva; egy nyomáskiegyenilto utat (50} amelyen keresztül a bemeneti kamra (2 b) és a tmuettyukeane «3-0 m adtató, <mvl· nymua^Uegtenkto t.‘ ι,Ο’ eg\. ,< h a p,my almenübe ! >'' nyíló nyílás véggel van ellátva; és egy, a lorgahyúfúd (40) és a nyomáskiegyenlító út (50) nyílásvége között található osztöelemot (32), ahol az osztódéin 0,0 t nngattymnd í ltl) akut a forgsftyűrdd (40) egyik oldalától a tórgattymud t-tó) manó, oldalán) hezodth, úgy, hogy legalább a íbrgattvúrúd (40) alsó részét lefedi; és ahol az obitároló kamrában < 33 ,pa nyílás vég a kenőanyag normal olajszintie fölött \au elkeNe/ve,FREE DALM REQUIREMENTS D K DUGΑ'ΠΎ OS COMPRESSOR 1 Piston Kilupn. amd fartahnaz. a ha 'ai 22 xx "k" (eg $ 1 egs k-putogo n nt a cylinder (32} and one (34 g of crankcase (34) has a lubricant) a lower part (56) formed as an oil storage chamber (35); a piston (36) disposed in the cylinder (32), a ratchet (40) being rotatable in the positive Gukamyah (34), and Battleship (33) through the piston 06) Connected, a pressure equilibrium path (50} through which the inlet chamber (2b) and the tmuettyukeane «3-0m transmitter, <mvl · nymu ^ Ubt. , With eg 'eg', <hap, my submenu>> ', an opening opening, and a dividing member (32) between the opening end of the groove rod (40) and the pressure compensating path (50), with its divisors 0, 0 t nngattymnd í ltl) acute on the side of the forgsftyűdd (40) on the side of the lake lakattattud tep) hezodth, so that it covers at least the lower part of the barrel (40), and where the aperture <33, the end of the opening is above the normal oil level of the lubricant, and 2, .Az 1, igenrpom vzninn dugattyú« kompresszor, tón) az osztódéin rö.O több osztólemezí (S4i tartalmaz, és a több osztólemez. (34) a torgtófynrud (40) tengelyiránya tpentén van-elrendezve,2, .The piston «1 compressor, toner» of the piston 1, yes, is divided into several divisions (contains S4i, and the multi-plate plate (34) is arranged in the pentene direction of the pin (40)). 3. A 2. Igénypont szerint; dngattvtts kompresszor, ahol az. osztólemezek (34; mindegyike tartalmaz: egy alsó reszt (éh) amelynek egy negyed henger (32) alakja van és a íorgattyúrdd i-Kb egy alsó oldala menten ívelt; és egy felső részt (58s< amely az alsó részben (56) folytatódik, és a forgaítymud (40) egyik oldalán van elhelyezve.3. According to claim 2; dngattvtts compressor where it is. dividing plates (34; each comprising: a lower cross (yaw) having a quarter cylinder (32) shape and a lower side of the pump crank i-Kb being curved; and an upper portion (58s <in the lower part (56) extending, and is located on one side of the forgaítymud (40). 4, Λ 3. igénypont szerinti dugattyús kompresszor, ahol a több osztólemez (54) a .(orgattyurésd (40) tengelyirányában egymás mellett tevő végrészei vastagságuk irányában ko,\f'k vöt ’he,kedo a dm ό' i <x tetemetölt atteenk egstt,,,^.A piston compressor according to claim 3, wherein the plurality of dividing plates (54) a. (In the axial direction of the orifice (40) in the direction of each other in the direction of their thickness, co? refuse egt ,,, ^. 5, Λ 4. igénypont szerinti dugattyús kompresszor, amely tartalmaz továbbá egy az, osztőlernezek (54.) közötti rések kozott elhelyezkedő és a résen átjutó kenőanyagot összegyűjtő gyűjtóelemétA reciprocating compressor according to claim 4, further comprising a collecting element for collecting the gaps between the slots (54) and the lubricant passing through the gap. 6, ÂZ .1, igénypont szerinti dugattyús kompresszor, amely tartálrnaz továbbá egy .oláj szeparátort (64) az elvaiuvto tag t5?i es a nyomási, tégy en'uto ut t5<v> nydawoge kezet-, aboi az oiajszeparátor (64) tartalmaz; egy labirintus reszt (66) amely az osztóelem (52) egy oldalán van kialakítva és egy kanyargós áramlást utat határoz meg; és eg\ meg,x fut' a ne \ „ mUavteg eg\ , dalán \<m k,Vakusa, e\ eys >ag\oö^ keresztmetszetű áramlási utat határoz üteg, mint a labiriutus rész ;66) által meghatározott áramlási űt.A reciprocating compressor according to claim 6, further comprising a .olai separator (64) for the displacement member 5a and the pressure, e. G. contain; a maze (66) formed on one side of the dividing member (52) and defining a winding flow path; and x, x runs' the flow path of the non-mUavteg eg, dal, m k, Vakusa, eys> g is a cross-sectional flow path as the labyrinth part;