Compressor, disc body and seal

Abstract

The invention relates to a compressor (10) having a stationary part (20) and a part (30) reciprocating along a main axis (X), and a leakage channel (L) extending axially between the stationary part (20) and the reciprocating part (30), wherein a plurality of chambers (50) are defined radially successively between the stationary part (20) and the reciprocating part (30) and extending annularly around the main axis (X), wherein a seal (60) closing or reducing the leakage channel (L) is arranged in at least one chamber (50). The compressor (10) has at least one bypass path (70, 70a, b, c, d) fluidly connecting two chambers (50).

Description

Technical Field

[0001] The present invention relates to a compressor, a disc-shaped body, a seal, and their use in a compressor. Background Technology

[0002] A reciprocating compressor typically includes a piston with a piston rod connected to it. The piston reciprocates within a cylinder liner and usually includes multiple piston rings as seals to seal the high-pressure side (i.e., the compression chamber) from the low-pressure side (i.e., the beginning of the piston rod).

[0003] Seals in the form of piston rod assemblies are also typically arranged to the piston rod. A piston rod assembly includes multiple chamber discs that are axially adjacent to each other and form chambers in which seals with one or more sealing rings are arranged. The sealing rings similarly seal the high-pressure side where the piston is located to the low-pressure side where the compressor drive is located.

[0004] A sealing assembly for a piston rod is known in US 3,544,118. DE 91 90 040 U1 and DE 10 2010034 870 A1 disclose seals in the field of internal combustion engines.

[0005] Piston compressors can be used to compress hydrogen. For example, hydrogen compression is necessary for hydrogen refueling stations. The required pressure there might be 400 bar for buses and 900 bar for passenger cars.

[0006] When refueling, the purity of the hydrogen is particularly important. Using lubricants will contaminate the hydrogen, which is undesirable. Therefore, a reciprocating compressor without lubrication (dry operation without lubricant) is preferred.

[0007] However, high pressure differentials and dry operation lead to very high wear. This applies to both the piston rings mounted on the piston and the sealing rings within the piston rod seals. The materials used for sealing have a so-called pv limit. Under high pressure differentials (p) and / or high speeds (v), there exists a limit beyond which wear increases disproportionately. Therefore, reaching or exceeding this limit is undesirable.

[0008] Because of the large pressure difference in the hydrogenation zone, the piston speed is limited, resulting in a long hydrogenation time. Summary of the Invention

[0009] The objective of this invention is to create the feasibility of compressing gases with high pressure differentials and high speeds.

[0010] This task is solved by a compressor intended to be protected according to the present invention.

[0011] The compressor includes a stationary component and a reciprocating component along a main axis, and an axially extending drain passage between the stationary and reciprocating components. Between the stationary and reciprocating components, a plurality of chambers are defined, arranged axially sequentially and extending annularly around the main axis. A seal is provided in at least one chamber to close or reduce the drain passage, i.e., to reduce or prevent leakage along the drain passage. The compressor is characterized by providing at least one bypass passage for fluid communication between two chambers.

[0012] Compressors, especially reciprocating compressors.

[0013] A leakage channel is typically present because the stationary and reciprocating parts do not come into contact. Seals reduce leakage along this channel, and to date, development has focused on further reducing leakage. In conventional piston rod seals, starting from the high-pressure side, the reduction of the dynamic pressure component primarily occurs in the first seal, while the reduction of the static pressure component primarily occurs in the last seal. Piston rings on the piston also have a similar effect. Therefore, the first and last seals bear the greatest load.

[0014] The inventors have recognized that, especially under high pressure differential conditions, it is preferable to distribute the applied pressure differential (the difference between the high-pressure side and the low-pressure side) more evenly across individual seals through a sealing device, i.e., an arrangement of multiple seals in multiple chambers arranged axially in sequence. As a result, the pressure differential (the pressure difference upstream and downstream of the seal) is reduced between the first and last seals. Consequently, the compressor can be designed so that no single seal reaches its pv limit during the intended period of use. Therefore, in this invention, the venting passage itself remains as closed as possible while providing a bypass passage specifically defined within the design scope that allows for predetermined leakage.

[0015] Therefore, the target leakage is achieved through a bypass or a bypass between individual chambers of the compressor, thereby achieving a uniform pressure distribution. The bypass is designed to achieve uniform pressure distribution through the arrangement of seals.

[0016] This invention can be used for sealing arrangements on compressor pistons and in compressor piston rod assemblies. Therefore, the stationary component can be a cylinder liner, and the reciprocating component can be a piston. Alternatively, the stationary component can be a sealing housing, and the reciprocating component can be a piston rod.

[0017] To achieve a uniform pressure distribution, a bypass fluid connection is preferably provided between two directly adjacent chambers. This causes leakage between the adjacent chambers, resulting in a pressure differential that is evenly distributed across all seals.

[0018] Since leakage is practically undesirable, only the amount of leakage through the bypass is permitted to be equal to the leakage required for the specified partial pressure balance. The amount of leakage through the bypass is specifically defined by its minimum cross-section, i.e., the cross-section at its narrowest point. It has been shown that the minimum cross-section M < 2 mm. 2 (square millimeters), especially M < 1.5 mm 2 This is preferred, especially in applications with a pressure differential > 300 bar. Preferably, the minimum cross-section is M > 0.1 mm. 2 .

[0019] Bypasses can be provided in stationary components, particularly in sealed housings, or in reciprocating components, particularly in pistons or seals. In seals, especially in the sealing ring or support ring, the introduction of holes and / or milling of portions is conceivable, thus enabling targeted leakage between chambers. As mentioned above, preferably, the holes / milling portions are not located in the area of ​​the leakage channel. If the seal is provided with a bypass, then the seal is preferably formed of a rigid material (e.g., plastics and / or metals with an elastic modulus > 5000 MPa) to achieve the targeted leakage.

[0020] In addition to the leakage channel, a bypass channel is specifically provided. In other words, the bypass channel is located where no leakage channel portion is formed. For example, in a sealing ring, the leakage channel portion is formed on the radial sealing surface because a small amount of leakage may occur there. In this case, for example, the bypass channel may preferably be formed laterally across the sealing ring, rather than in the area of ​​the sealing surface.

[0021] The bypass passage is preferably formed by at least one hole. The hole's size can be precisely adjusted, so the minimum cross-section can be essentially defined by the hole's diameter, thus determining the leakage. Simultaneously, the hole is relatively easy to manufacture, therefore, the manufacturing cost of the compressor does not significantly increase. A single hole can also typically be formed in multiple drilling processes, and then, for example, include kinks. The hole need not be straight.

[0022] The piston can be referred to as an assembled piston or a piston with a one-piece piston body. An assembled piston comprises multiple disc-shaped bodies in the form of piston discs, arranged sequentially in the axial direction and forming a piston body together, optionally supplemented by more disc-shaped bodies. Whether one-piece or assembled, the piston body preferably comprises a cylindrical core and multiple annular protrusions extending around the core, with radially outward channels formed between these protrusions for sealing. The channels are partially closed by a cylinder liner, with the remaining clearance forming a portion of the venting passage. Thus, these channels, together with the cylinder liner, form a sealed chamber for sealing.

[0023] The piston rod assembly is typically "built-in" and then comprises multiple disc-shaped bodies in the form of axially arranged chamber discs, each disc including a central bore and forming a sealed housing through which the piston rod extends. The chamber discs form multiple radially inward channels that are partially closed by the piston rod, thus the remaining clearance forms part of a drainage channel. In this case, the channels, together with the outer peripheral surface of the piston rod, form a chamber for sealing.

[0024] The disc-shaped objects can be twisted together.

[0025] Therefore, in an advantageous embodiment, the piston or sealing housing includes a plurality of axially sequentially arranged discs, each disc including a first axial surface and a second axial surface arranged opposite to each other, and a radial surface, and a hole extending between and / or between the first axial surface and the radial surface. The radial surface is an inner radial surface in the case of the sealing housing and an outer radial surface in the case of the piston. The radial surface may also be the bottom of a channel forming a passage, and then may also be referred to as the bottom of a chamber forming a cavity.

[0026] Multiple holes can also be set in different components.

[0027] Especially in the case of seals and discs, at least a portion of the hole preferably extends parallel to the main axis, which simplifies the manufacturing of the hole.

[0028] If the piston comprises a cylindrical core and a plurality of annular protrusions extending circumferentially around the core, then at least a portion of the bore preferably extends through the core. Thus, for example, the bottoms of two channels in adjacent chambers can be connected to each other by drilling through the core. The bore extends through the center of the piston, and therefore intersects the main axis.

[0029] In some embodiments, a bypass passage is directly disposed in the drainage channel region, particularly in the form of a groove. This bypass passage is particularly suitable for placement within a disc-shaped body, especially preferably in the region of the sealing surface. The sealing surface is preferably horizontal, and the bypass passage is a groove. Preferably, the corresponding sealing surface of the seal is also horizontal. Preferably, the sealing surface extends perpendicular to the main axis. The groove preferably extends perpendicular to the main axis. As mentioned above, if a cut is provided in the seal, the gradual wear of the seal will progressively cause the bypass passage to become smaller. A groove in a less worn sealing fitting (disc-shaped body) will not become smaller over time, or will become very small. The bypass passage in the disc-shaped body in the drainage channel region, especially on the sealing surface, thus maintains its predetermined cross-section for a long period. Therefore, a groove represents a preferred embodiment of the bypass passage.

[0030] The minimum cross-section required for a bypass is very small. Manufacturing an orifice with this cross-section is technically challenging, especially due to its length-to-diameter ratio. Therefore, in advantageous embodiments, a throttling element is arranged in an orifice or channel, defining the minimum cross-section M of the bypass. In this case, the orifice itself does not need to be particularly narrow, and thus can be manufactured more easily. Preferably, the throttling element does not extend to the entire length of the orifice. This results in a more advantageous length-to-diameter ratio for the throttling orifice disposed in the throttling element, which can then be easily manufactured using precision mechanics. Particularly preferably, the throttling element is a threaded connection with a perforated plate screwed into the orifice, or an insert with a perforated plate inserted into a channel. In the perforated plate, orifices with very small cross-sections can be produced particularly easily.

[0031] Throttling elements can also include porous materials. The porous material and the diameter of the holes or the cross-section of the channels are then combined to form the required minimum cross-section.

[0032] The greater the pressure difference between two adjacent chambers, the smaller the bypass passage should be, because even a small bypass passage is sufficient for pressure equalization at higher pressure differences. Therefore, advantageous embodiments provide multiple bypass passages, where, in the case of two adjacent bypass passages, the minimum cross-sectional area M of the bypass passage arrangement closer to the high-pressure side of the compressor is less than or equal to the minimum cross-sectional area M of the bypass passage arrangement closer to the low-pressure side of the compressor. In other words, the bypass passages increase or at least remain constant from the high-pressure side to the low-pressure side. Particularly preferably, the bypass passage orifices are consistent, especially identical, and the differences in the bypass passages are achieved by the throttling element used in each case. The throttling elements are designed differently and include different minimum cross-sectional areas.

[0033] The object of the invention is also addressed by a disc-shaped body designed for use in a compressor, comprising a first axial surface, a second axial surface, and a radial surface arranged opposite to each other with respect to the disc, characterized in that a bypass passage extends between and / or between the first and second axial surfaces. The radial surface is particularly an inner or outer radial surface. Preferably, the bypass passage of the disc-shaped body is a hole.

[0034] The objective of this invention is also achieved by a disc-shaped body designed for use in a compressor, comprising an inner radial surface and an outer radial surface, with a bypass passage extending between the inner and outer radial surfaces. The bypass passage of this disc-shaped body is preferably a channel.

[0035] The disc-shaped body can be further formed in the manner described above with respect to the compressor.

[0036] The objective of this invention is also achieved by a seal designed for use in a compressor, having a first axial end face, a second axial end face, a radial inner surface, and a radial outer surface, with a bypass extending between at least two surfaces, namely the first axial end face, the second axial end face, the radial inner surface, and the radial outer surface.

[0037] The seal can also be further formed in the manner described above with respect to the compressor.

[0038] The objective of the present invention can also be achieved by using a disc-shaped body or seal as described above in a compressor, preferably a reciprocating compressor, especially in a compressor as described above. Attached Figure Description

[0039] The invention will now be described and explained by way of example with reference to the accompanying drawings. It shows that:

[0040] Figure 1 A partial cross-sectional view of the first embodiment of the compressor;

[0041] Figure 2 A partial cross-sectional view of a second embodiment of the compressor;

[0042] Figure 3 A partial cross-sectional view of the third embodiment of the compressor;

[0043] Figure 3A Figure 3 The local area A shown;

[0044] Figure 4 Perspective view of the support ring used in the compressor;

[0045] Figure 5 A partial cross-sectional view of the fourth embodiment of the compressor;

[0046] Figure 6 A partial perspective view of the discoid body.

[0047] Figure Labels

[0048] 10 Compressors

[0049] 20 Fixed components

[0050] 30 Reciprocating motion components

[0051] 40 discoid bodies

[0052] 50 chambers

[0053] 60 seal

[0054] 70 Bypass

[0055] 70a Bypass

[0056] 70b Bypass

[0057] 70c bypass

[0058] 70d bypass

[0059] 72 holes

[0060] 74 Throttling components

[0061] 76-hole plate

[0062] 78 channels

[0063] 120 cylinder liner

[0064] 122 Sliding Surface

[0065] 130 Piston

[0066] 132 substrate

[0067] 140 Piston Disc

[0068] 150 Piston Body

[0069] 152 core components

[0070] 154 protrusions

[0071] 156 Channel

[0072] 160 piston rings

[0073] 182 First Axial Surface

[0074] 184 Second Axial Surface

[0075] 186 outer diameter surface

[0076] 220 Sealed enclosure

[0077] 222 substrate

[0078] 223 Main chamber ring

[0079] 224 Cover Plate

[0080] 226 end plate

[0081] 228 Channel

[0082] 230 Piston Rod

[0083] 240 chamber disc

[0084] 262 Support ring

[0085] 264 Sealing Ring

[0086] 266 Cap Ring

[0087] 270 Hose Spring

[0088] 272 First Axial End Face

[0089] 274 Second Axial End Face

[0090] 276 Radial inner surface

[0091] 278 Radial outer surface

[0092] 282 First Axial Surface

[0093] 284 Second Axial Surface

[0094] 286 Radial inner surface

[0095] 288 Sealing surface

[0096] H High-voltage side

[0097] N Low-pressure side

[0098] L-channel

[0099] X Main axis Detailed Implementation

[0100] Figure 1 The compressor 10 shown in detail includes a cylinder liner 120 as a stationary component 20 and a piston 130 as a reciprocating component 30. During normal use, the piston 130 reciprocates relative to the cylinder liner 120 along the main axis X between the high-pressure side H and the low-pressure side N.

[0101] The cylinder liner 120 includes a sliding surface 122, which is a surface with an inner cylindrical circumference.

[0102] Piston 130 is referred to as assembled piston 130. Piston 130 includes a plurality of disc-shaped bodies 40, namely, a base plate 132 and a plurality of piston discs 140 arranged axially in succession. Piston 130 is connected to a piston rod 230. The piston discs 140 and the base plate 132 form a piston body 150. Piston body 150 includes a cylindrical core 152 and a plurality of annular protrusions 154 extending circumferentially around the core 152. A plurality of channels 156 are formed between the protrusions 154, each channel 156 being formed by two piston discs 140 or by the piston discs 140 and the base plate 132. The channels 156 are partially closed by a cylinder liner 120, thereby forming a plurality of chambers 50 arranged axially in succession and extending annularly around a main axis together with the cylinder liner 120. The cylinder liner 120 does not contact the piston body 150. This leaves an axially oriented drainage channel L between the cylinder liner 120 and the piston 130.

[0103] Leakage along the venting channel L is generally undesirable, but usually cannot be completely avoided. However, leakage can be minimized. To this end, a seal 60 is arranged in each chamber 50, which can seal off or reduce the leakage channel L. In the illustrated embodiment, the seal 60 is a piston ring 160, shown here in a simplified form. Depending on the direction of movement of the piston 130 at any given time, the piston ring 160 contacts either the high-pressure side or the low-pressure side of the channel 156, and seals the leakage channel L there.

[0104] In a conventional sealing arrangement with piston rings 160, the dynamic pressure component at the first seal 60 and the static pressure component at the last seal 60 decrease, starting from the high-pressure side H. To avoid this, three bypass passages 70a, b, and c are provided in addition to the venting passage L. Each bypass passage 70a, b, and c fluidly connects two directly adjacent chambers 50.

[0105] Bypasses 70a, b, and c each include a bore 72 parallel to the main axis X. In the illustrated embodiment, bypasses 70a, b, and c extend through a protrusion 154, i.e., from a first axial surface 182 of piston disc 140 to a second axial surface 184 of an opposing piston disc 140. Thus, each bore 72 connects two adjacent chambers 50. The bores 72 actually have a small diameter, shown enlarged here. Each piston disc 140 also includes an outer diameter surface 186.

[0106] In addition to the venting channel L, bypass passages 70a, b, and c provide the possibility for the gas on the high-pressure side to flow into its respective next chamber 50. In this way, the pressure difference between the high-pressure side H and the low-pressure side N is gradually reduced and becomes uniform overall.

[0107] exist Figure 2 In the embodiment shown in detail, the piston 30 has a one-piece piston body 150. The piston body 150 also includes a cylindrical core 152 and a plurality of annular protrusions 154 extending circumferentially around the core 152. The design of the cylinder liner 20, piston rod 230, and seal 60 is consistent with... Figure 1 The embodiments shown are the same.

[0108] According to Figure 2In this embodiment, bypass passages 70a, b, and c are also formed by holes 72. However, holes 72 do not extend parallel to the main axis X. Hole 72 extends linearly from the bottom of channel 156 to the bottom of channel 156. Instead, hole 72 extends linearly from the bottom of channel 156 to the bottom of the adjacent channel 156. Hole 72 extends completely through the core 152 of piston body 150. In this case, the hole passes through the main axis X. In this embodiment, adjacent chambers 50 are also connected through holes 72, thereby creating a uniform pressure distribution on all seals 60.

[0109] Figure 3 A portion of the compressor 10 is shown, which includes a sealed housing 220 as a stationary component 20 and a piston rod 230 as a reciprocating component 30. The piston rod 230 reciprocates relative to the sealed housing 220 along the main axis X between the high-pressure side H and the low-pressure side N.

[0110] The sealed housing 220 includes more than 40 chamber discs 240 as disc-shaped bodies, namely a base plate 222, multiple main chamber discs 223, a top plate 224, and an end plate 226, which are arranged adjacent to each other along the main axis X. Each chamber disc 240 includes a central hole. A piston rod 230 extends through the central hole. Every two adjacent chamber discs 240 together form a radially inwardly opening channel 228.

[0111] The channel 228 of the chamber disk 240 is partially closed by the piston rod 230. In this way, the chamber disk 240 and the piston rod 230 form a plurality of chambers 50 arranged axially and extending in a ring around the main axis, wherein a drainage channel L is left between the chamber disk 240 and the piston rod 230.

[0112] Each chamber disc 240 includes a first axial surface 282 and a second axial surface 284 arranged opposite to each other with respect to the piston disc 240, and an inner radial surface 286 (see Figure 3A ).

[0113] Each of the four chambers 50 is equipped with a sealing element 60. Each sealing element 60 includes a support ring 262, a sealing ring 264, and a cover ring 266 (see...). Figure 3A Sealing ring 264 and cap ring 266 are secured to piston rod 230 by hose spring 270. In other embodiments, seal 60 may have different structures and include more or fewer rings. Support ring 262 does not contact piston rod 230 during normal use, but is arranged radially spaced from piston rod 230. Pressure from the high-pressure side H presses seal 60 against chamber ring 240, which is closer to the low-pressure side N. Support ring 262 supports seal 60 to chamber ring 240 in the axial direction.

[0114] The sealing ring 264 is adjacent to the piston rod 230, thereby sealing the venting passage L, thus completely or partially closing the venting passage L.

[0115] In addition to the effluent channel L, four bypass channels 70a, b, c, and d are provided, each of which fluidly connects two adjacent chambers 50 (see...). Figure 3 Bypasses 70a, b, c, and d are formed by orifice 72 (see...). Figure 3A The hole 72 extends between the first axial surface 282 and the inner radial surface 286, thereby connecting adjacent chambers 50.

[0116] In each orifice 72, a throttling element 74 in the form of a threaded connector with a perforated plate 76 is arranged and screwed into the orifice 72. The orifice plate 76 includes holes defining the minimum cross-section of each bypass passage 70a, b, c, d. Starting from the high-pressure side H, the holes of the orifice plate 76 of the bypass passages 70a, b, c, d have diameters of 0.4 mm, 0.4 mm, 0.5 mm, and 0.6 mm, respectively. Therefore, the minimum cross-section from bypass passages 70a, b, c, d to bypass passages 70a, b, c, d becomes smaller or remains constant in the direction toward the high-pressure side H.

[0117] For example, Figure 4 The support ring 262 shown can be inserted into Figure 3 In the piston housing 220 shown, the support ring 262 includes a first axial end face 272, a second axial end face 274 arranged opposite to each other, a radial inner surface 276, and a radial outer surface 278.

[0118] The support ring 262 also includes a bypass passage 70 in the form of a hole 72. The hole 72 extends radially from the radially inner surface 276 to the radially outer surface 278. During normal use, as described above, the radially inner surface 276 of the support ring 262 is not adjacent to the piston rod 230. Additionally, the support ring 262 is not adjacent to the radially outer surface 278 of the sealing housing 220. Thus, the bypass passage 70 of the support ring 262 also connects two adjacent chambers 50 (see...). Figure 3A ).

[0119] Figure 5 A portion of compressor 10 is shown, which is related to... Figure 3 The compressor 10 shown is partially identical. The compressor 10 includes a sealed housing 220 as a stationary component 20 and a piston rod 230 as a reciprocating component 30. The piston rod 230 reciprocates relative to the sealed housing 220 along the main axis X between the high-pressure side H and the low-pressure side N.

[0120] The sealed housing 220 includes a plurality of chamber discs 240 forming a disc body 40, namely a base plate 222, a plurality of main chamber discs 223, a top plate 224, and an end plate 226, which are arranged adjacent to each other along the main axis X. Each chamber disc 240 includes a central hole. A piston rod 230 extends through the central hole. Every two adjacent chamber discs 240 together form a radially inwardly opening channel 228.

[0121] The channel 228 of the chamber disk 240 is partially closed by the piston rod 230. Thus, the chamber disk 240 and the piston rod 230 form a plurality of chambers 50 arranged sequentially in the axial direction and extending annularly around the main axis, wherein a drainage channel L is left between the chamber disk 240 and the piston rod 230.

[0122] Each chamber disc 240 includes a first axial surface 282 and a second axial surface 284 arranged opposite to the piston disc 240, and an inner radial surface 286.

[0123] Each of the four chambers 50 is equipped with a seal 60. Each seal 60 includes a support ring 262, a sealing ring 264, and a cover ring 266 (see...). Figure 3A Sealing ring 264 and cap ring 266 are secured to piston rod 230 by hose spring 270. In other embodiments, seal 60 may have different structures and include more or fewer rings. Support ring 262 does not contact piston rod 230 during normal use, but is arranged radially spaced from piston rod 230. Pressure from the high-pressure side H presses seal 60 against a first axial surface 282 of chamber disc 240. The first axial surface 282 thereby forms sealing surface 288. Support ring 262 supports seal 60 in the axial direction, keeping it in close contact with chamber disc 240.

[0124] The sealing ring 264 is adjacent to the piston rod 230, thereby sealing the discharge passage L, that is, it completely or partially closes the discharge passage L.

[0125] In the region of the drain channel L, a bypass passage 70 in the form of a channel 78 is provided, which fluidly communicates with two adjacent chambers 50. The channel 78 extends in a first axial surface 282, which is also the sealing surface 288. In this case, the channel 78 extends radially completely through the sealing surface 288. Even though the entire surface of the seal 60 is adjacent to the sealing surface 288, the channel 78 remains open in this manner, forming the bypass passage 70.

[0126] Figure 6 The disc-shaped body 40 is a chamber disc 240 (not shown in detail) for the compressor. The structure of the chamber disc 240 is similar to... Figure 5 The chamber disc 240 shown is similar.

[0127] The chamber disc 240 includes a central bore surrounded by an inner radial surface 286. The chamber disc 240 also has a first axial surface 282, which is also a sealing surface 288 (not shown) used as a seal. During normal use, the seal is adjacent to the sealing surface 288.

[0128] A sealing surface 288 is disposed to an axial protrusion of the chamber disc 240. The axial protrusion includes an outer radial surface 186.

[0129] The chamber disc 240 includes a bypass passage 70 in the form of a channel 78. The channel 78 extends from the outer radial surface 186 to the inner radial surface 286. If the seal is adjacent to the sealing surface 288, gas can continue to flow through the seal through the bypass passage 70. The dimensions of the bypass passage 70 are predetermined to achieve the desired leakage.

[0130] The channel 78 extends radially, that is, perpendicular to the main axis of the chamber disk 240.

Claims

1. A compressor (10) having a stationary component (20) and a component (30) reciprocating along a main axis (X), and a venting passage (L) extending axially between the stationary component (20) and the reciprocating component (30), A plurality of chambers (50) are defined between the fixed component (20) and the reciprocating component (30), which are axially arranged sequentially and extend circumferentially around the main axis (X). The feature is that at least one chamber (50) is provided with a seal (60) for closing or reducing the leakage passage (L), characterized in that, Multiple bypass passages (70, 70a, b, c, d) are provided for fluid communication between two chambers (50). Among the two adjacent bypass passages (70, 70a, b, c, d), the minimum cross-section M of the bypass passage (70, 70a, b, c, d) arranged near the high-pressure side (H) of the compressor (10) is smaller than the minimum cross-section M of the bypass passage (70, 70a, b, c, d) arranged near the low-pressure side (N) of the compressor (10).

2. The compressor (10) according to claim 1, characterized in that, The fixed component (20) is a cylinder liner (120), and the reciprocating component (30) is a piston (130), or the fixed component (20) is a sealed housing (220), and the reciprocating component (30) is a piston rod (230).

3. The compressor (10) according to claim 1 or 2, characterized in that, The bypass passages (70, 70a, b, c, d) provide fluid communication between two directly adjacent chambers (50).

4. The compressor (10) according to claim 1 or 2, characterized in that, The bypass pathways (70, 70a, b, c, d) include a minimum cross-section M of less than 2 square millimeters.

5. The compressor (10) according to claim 1 or 2, characterized in that, The bypass passages (70, 70a, b, c, d) are provided in the fixed component (20), the reciprocating component (30), or the seal (60).

6. The compressor (10) according to claim 1 or 2, characterized in that, In addition to the drainage channel (L), the bypass channels (70, 70a, b, c, d) are also provided.

7. The compressor (10) according to claim 2, characterized in that, The bypass passages (70, 70a, b, c, d) are formed by at least one hole (72).

8. The compressor (10) according to claim 7, characterized in that, The piston (130) or the sealing housing (220) includes a plurality of axially arranged discs (40), wherein each disc (40) has a first axial surface (182, 282) and a second axial surface (184, 284) arranged opposite to each other with respect to the disc (40), and a radial surface (186, 286), wherein the hole (72) extends between the first axial surface (182, 282) and the radial surface (186, 286) and / or between the first axial surface (182, 282) and the second axial surface (184, 284).

9. The compressor (10) according to claim 8, characterized in that, At least a portion of the hole (72) extends parallel to the main axis (X).

10. The compressor (10) according to claim 9, characterized in that, The piston (130) includes a cylindrical core (152) and a plurality of annular protrusions (154) extending circumferentially around the core (152), and at least a portion of the hole (72) extends through the core (152).

11. The compressor (10) according to claim 7, characterized in that, The bypass passages (70, 70a, b, c, d) are located in the area of ​​the discharge channel (L).

12. The compressor (10) according to claim 11, characterized in that, The bypass passages (70, 70a, b, c, d) are channels (78).

13. The compressor (10) according to claim 12, characterized in that, The piston (130) or the sealing housing (220) includes a plurality of discs (40) arranged sequentially along the axial direction, wherein the discs (40) include a sealing surface (288) and the channel (78) extends within the sealing surface (288).

14. The compressor (10) according to claim 13, characterized in that, A throttling element (74) is arranged in the hole (72) or the channel (78), which defines the minimum cross-section M of the bypass passage (70, 70a, b, c, d).

15. The compressor (10) according to claim 14, characterized in that, The throttling element (74) is a threaded connector with the hole (72) screwed into the orifice plate (76), or the throttling element (74) is an insert with the orifice plate (76) inserted into the channel (78).

16. The compressor (10) according to claim 14 or 15, characterized in that, The throttling element (74) comprises a porous material.

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