Compressor, disk body and seal

Abstract

The compressor (10) comprises a stationary part (20), a part (30) that reciprocates along a main axis (X), and a leakage path (L) extending axially between the stationary part (20) and the reciprocating part (30), with a plurality of chambers (50) that are axially arranged one behind the other and extend annularly around the main axis (X) being defined between the stationary part (20) and the reciprocating part (30), and a seal (60) that closes or reduces the leakage path (L) is disposed within at least one of the chambers (50). The compressor (10) has at least one bypass (70, 70a, 70b, 70c, 70d) that fluidly connects the two chambers (50) to each other.

Description

Technical Field

[0001] The present invention relates to a compressor, a disk body, a seal, and the use of the disk body and the seal in a compressor.

[0002] A piston compressor usually has a piston with a piston rod following the piston. The piston reciprocates within a sleeve and usually has a plurality of piston rings as seals, and these piston rings seal the high-pressure side, i.e., the compression chamber, from the low-pressure side, i.e., where the piston rod starts.

[0003] A seal in the form of a piston rod packing is also usually arranged on the piston rod. The piston rod packing has a plurality of chamber disks, and these chamber disks are in contact with each other in the axial direction and form a plurality of chambers. A seal with one or more seal rings is arranged in these chambers. Similarly, the seal rings seal the high-pressure side where the piston is located from the low-pressure side where the compressor drive is located.

[0004] The seal packing for the piston rod is known from U.S. Patent No. 3,544,118. Seals in the field of internal combustion engines are disclosed in German Utility Model No. 9,190,040 and German Patent Application Publication No. 10 2010 034 870.

[0005] A piston compressor can be used to compress hydrogen. The compression of hydrogen is necessary, for example, for a hydrogen refueling station. The required pressure can be, for example, 400 bar for buses and 900 bar for passenger cars.

[0006] In refueling, the purity of hydrogen is particularly crucial. The use of lubricants may contaminate hydrogen, which is not desirable. Therefore, preferably, a non-lubricated piston compressor is desirably used (dry operation without lubricant).

[0007] However, large pressure differences and dry operation lead to extremely high wear. This applies to both the piston rings on the piston and the seal rings within the piston rod seal. The materials used for the seals have a so-called limiting PV value. A limit exists when the pressure difference (p) is large and / or the velocity (v) is high, and beyond this limit, wear increases excessively. Therefore, it is undesirable to reach or exceed this limit.

[0008] In the field of hydrogen refueling, a large pressure difference limits the piston speed, which can lead to longer refueling times.

[0009] The object of the present invention was to provide a means that enables the compression of gas by a large pressure difference and high speed.

[0010] This problem is solved by the compressor described in claim 1.

[0011] The compressor has a stationary section, a section that reciprocates along a main axis, and a leakage path extending axially between the stationary section and the reciprocating section. Between the stationary section and the reciprocating section, a plurality of chambers are defined, extending annularly around the main axis and arranged sequentially in the axial direction. A seal is provided in at least one chamber to close or reduce the leakage path, that is, to reduce or prevent leakage along the leakage path. The compressor is characterized by having at least one bypass that fluidly connects two chambers to each other.

[0012] The compressor is, in particular, a piston compressor.

[0013] Leakage paths inherently exist because stationary and reciprocating parts do not come into contact. Seals reduce leakage along these paths, and traditionally, development has focused on further reducing leakage. In the case of conventional piston rod seals, starting from the high-pressure side H, the dynamic pressure component reduction primarily occurs at the first seal, while the static pressure component reduction primarily occurs at the last seal. The same applies to piston rings in a piston. In other words, the first and last seals are subjected to the greatest load.

[0014] The inventors realized that, especially when the pressure difference is large, it is progressive to distribute the pressure difference (the difference between the high-pressure and low-pressure sides) applied across a seal unit—that is, a unit consisting of multiple seals in multiple chambers arranged sequentially in the axial direction—more uniformly across the individual seals. This reduces the pressure difference between each seal (the pressure difference before and after the seal) between the first and last seals. As a result, the compressor can be designed so that, when used as specified, no seal reaches the critical PV value. In other words, the present invention ensures that the leak path itself is still closed as well as possible, while a bypass is provided that allows for a predetermined leak, specifically defined within the design framework.

[0015] Therefore, uniform pressure distribution is achieved through appropriate leakage via one or more bypasses between the individual chambers of the compressor. The bypasses are designed to ensure uniform pressure distribution across the sealing units.

[0016] The present invention can be used in both a seal unit provided on the piston of a compressor and a piston rod packing of a compressor. Therefore, the stationary part may be a sleeve, and the reciprocating part may be a piston. Alternatively, the stationary part may be a packing casing, and the reciprocating part may be a piston rod.

[0017] For uniform pressure distribution, it is significant that the bypass fluidly connects two immediately adjacent chambers. This creates a leak between each adjacent chamber, thereby uniformly distributing the pressure difference across all seals.

[0018] Leakage is undesirable, so only the amount of leakage necessary for the specified partial pressure compensation is allowed through the bypass. Leakage through the bypass is defined in particular by the minimum cross-section of the bypass, i.e., the cross-section of the narrowest part of the bypass. Especially in the operating range where the pressure difference exceeds 300 bar, 2 mm 2 Minimum cross-sectional area M less than 1.5 mm 2 It was found that M less than 0.1 mm is progressive. The minimum cross-sectional area M is preferably 0.1 mm 2 It is larger than that.

[0019] Bypasses may be provided in stationary parts, particularly packing casings, or in reciprocating parts, particularly pistons, or within seals. In seals in particular, holes and / or milled sections may be formed in the seal ring or support ring to allow for proper leakage between chambers. As described above, preferably the holes / milled sections are not located in the area of ​​the leakage path. If a bypass is provided in a seal, the seal is preferably formed from a rigid material (e.g., plastics and / or metals with an elastic modulus greater than 5000 MPa) to achieve proper leakage.

[0020] Bypasses are provided in addition to the leak path, specifically in areas where no portion of the leak path is formed. At the seal ring, for example, a portion of the leak path is formed in contact with the radial seal surface, because a small amount of leakage may occur there. In such cases, the bypass can be created, for example, preferably penetrating the seal ring laterally, but not in the area of ​​the seal surface.

[0021] The bypass is preferably formed by at least one hole. The hole can be precisely controlled in terms of its size, so that the minimum cross-section and thus leakage can be defined solely by the diameter of the hole. At the same time, since the hole can be manufactured relatively easily, the manufacturing cost of the compressor does not increase significantly. A single hole may be formed in essentially multiple drilling processes, in which case it may have, for example, a bend. In other words, the hole does not necessarily have to be straight.

[0022] The piston may be a so-called assembly piston or a piston with a single piston body. An assembly piston has multiple disc bodies in the form of piston discs, which are arranged sequentially in the axial direction and together optionally supplemented by other disc bodies to form the piston body. The piston body, whether in a single or assembly form, preferably has a cylindrical core and multiple annular projections that surround and extend around the core in the circumferential direction, with radially outward grooves for sealing formed between these projections. The grooves are partially closed by a sleeve, in which case the remaining gap forms a portion of the leak path. Thus, the grooves, together with the sleeve, form a chamber for sealing.

[0023] The piston rod packing is essentially an "assembly type," in which it has multiple disc bodies in the form of a chamber disc. These disc bodies are arranged axially, one in front of the other, and each has a central hole, forming a packing casing through which the piston rod extends. The chamber disc has multiple radially inward grooves, which are partially closed by the piston rod, and again, the remaining gaps form a portion of the leak path. The grooves, together with the circumferential surface of the piston rod, form a chamber for sealing.

[0024] The disc bodies can be fastened together with screws.

[0025] Thus, in an advantageous refinement, the piston or the packing casing has a plurality of disk bodies arranged axially one behind the other, in which case the disk bodies have a first axial face, a second axial face arranged on the opposite side with respect to the disk body, and a radial face, and holes extend between the first axial face and the radial face and / or between the first axial face and the second axial face. The radial face is the inner radial face in the case of the packing casing or the outer radial face in the case of the piston. The radial face may be the bottom of a formed groove, in which case this groove bottom may also be called the chamber bottom of a formed chamber.

[0026] A plurality of holes may be provided in different components.

[0027] The holes preferably extend at least partially parallel to the main axis, particularly in the case of seals and disk bodies. This facilitates the manufacture of the holes.

[0028] If the piston has a cylindrical core and a plurality of annular protrusions that extend circumferentially around the core, the holes preferably extend at least partially through the core. In this way, by drilling through the core transversely, for example, the two groove bottoms of adjacent chambers can be connected to each other. The holes particularly preferably extend through the center of the piston, i.e., the holes intersect the main axis.

[0029] In some embodiments, the bypass is provided directly in the area of the leakage path, particularly in the form of a groove. Such a bypass can be provided particularly on the disk body, preferably in the area of the sealing surface. In this case, the sealing surface is preferably flat and the bypass is a groove. The sealing surface of the corresponding seal is also preferably flat as well. One or more sealing surfaces preferably extend perpendicular to the main axis. The groove preferably extends perpendicular to the main axis. As described above, when a milling part is provided on the seal, the bypass gradually becomes smaller due to the progress of wear of the seal. The groove provided in the wear-resistant seal partner (disk body) hardly becomes smaller or only extremely slightly over time. Therefore, the bypass provided on the disk body, particularly on the sealing surface, within the area of the leakage path maintains its predefined cross-section over a long period of time. That is, this groove constitutes one preferred embodiment of the bypass.

[0030] The targeted minimum cross-section of the bypass is extremely small. Manufacturing a hole having such a cross-section is technically difficult, particularly based on the ratio of its length to its diameter. Therefore, in a preferred improvement, a throttle that defines the minimum cross-section M of the bypass is arranged within the hole or the groove. In this case, the hole itself does not particularly need to be narrow and can be manufactured relatively easily. The throttle preferably does not extend over the entire length of the hole. Thereby, a more suitable ratio of the length to the diameter of the throttle hole existing within the throttle is obtained, and in this case, the throttle hole can be easily manufactured by precision machinery. Particularly preferably, the throttle is a screwed-in member with a perforated plate screwed into the hole or an inserted member with a perforated plate inserted into the groove. A hole having an extremely small cross-section can be particularly easily produced in the perforated plate.

[0031] The throttle may contain a porous material. In this case, the porous material and the diameter of the hole or the cross-section of the groove are formed together to produce the desired minimum cross-section.

[0032] The larger the pressure difference between two adjacent chambers, the smaller the bypass is desirable. This is because, for pressure compensation, a smaller bypass is already sufficient for larger pressure differences. Therefore, an advantageous improvement is to provide multiple bypasses, in which case, of each pair of adjacent bypasses, the bypass closer to the high-pressure side of the compressor has a minimum cross-sectional area M that is smaller than or equal to that of the bypass closer to the low-pressure side of the compressor. In other words, the bypasses increase in size from the high-pressure side to the low-pressure side, or at least remain unchanged. Particularly preferable are the bypass holes of the same type, and especially identical, and the differences between the bypasses are obtained by the throttles inserted in each. That is, the throttles are configured in various ways, and especially each has a different minimum cross-sectional area.

[0033] The problems of the present invention can also be solved by a disk body formed for use in a compressor, having a first axial surface, a second axial surface located opposite to the disk body, and a radial surface, characterized by a bypass extending between the first axial surface and the radial surface and / or between the first axial surface and the second axial surface. The radial surface is either an inner radial surface or an outer radial surface. The bypass of the disk body is preferably a hole.

[0034] The problem of the present invention can also be solved by a disk body formed for use in a compressor, having an inner radial surface and an outer radial surface, with a bypass extending between the inner radial surface and the outer radial surface. The bypass of this disk body is preferably a groove.

[0035] The disk body may be further improved with respect to the compressor as described above.

[0036] The problem of the present invention can also be solved by a seal formed for use in a compressor, comprising a first axial end face, a second axial end face, a radial inner surface, and a radial outer surface, characterized by a bypass extending between at least two of these surfaces, i.e., the first axial end face, the second axial end face, the radial inner surface, and the radial outer surface.

[0037] The seal may be further improved as described above with respect to the compressor.

[0038] The problems of the present invention can also be solved by using a compressor, preferably a piston compressor, and more particularly a compressor according to the above description, by using a disk body or seal according to the above description.

[0039] The present invention will be described below with reference to the drawings. [Brief explanation of the drawing]

[0040] [Figure 1] This is a cross-sectional view showing a part of the first embodiment of the compressor. [Figure 2] This is a cross-sectional view showing a part of the second embodiment of the compressor. [Figure 3] This is a cross-sectional view showing a part of the third embodiment of the compressor. [Figure 3A] This is a detailed view of part A shown in Figure 3. [Figure 4] This is a perspective view showing a support ring for a compressor. [Figure 5] This is a cross-sectional view showing a part of the first embodiment of the compressor. [Figure 6] This is a perspective view showing a portion of the disk.

[0041] The compressor 10, partially shown in Figure 1, has a sleeve 120 as a stationary part 20 and a piston 130 as a reciprocating part 30. When used as specified, the piston 130 reciprocates along the main axis X relative to the sleeve 120 between the high-pressure side H and the low-pressure side N.

[0042] The sleeve 120 has a sliding surface 122, which is a cylindrical circumferential surface located on the inside.

[0043] The piston 130 is a so-called assembly-type piston 130. The piston 130 has a plurality of disc bodies 40, namely a base plate 132 and a plurality of piston discs 140 arranged sequentially front to back in the axial direction. The piston 130 is coupled to a piston rod 230. The piston discs 140 together with the base plate 132 form a piston body 150. The piston body 150 has a cylindrical core 152 and a plurality of annular projections 154 that surround and extend around the core 152 in the circumferential direction. A plurality of grooves 156 are formed between the projections 154, and each groove 156 is formed by two piston discs 140 or by one piston disc 140 and the base plate 132. The grooves 156 are partially closed by sleeves 120, so that the piston body 150 together with sleeves 120 forms a plurality of chambers 50 that are arranged sequentially front to back in the axial direction and extend annularly around the main axis. In this case, the sleeve 120 is not in contact with the piston body 150. As a result, an axially extending leakage path L remains between the sleeve 120 and the piston 130.

[0044] Leakage along the leak path L is generally undesirable, but usually cannot be completely avoided. However, it can be minimized. To this end, a seal 60 is placed within each chamber 50 to close or reduce the leak path L. In the illustrated embodiment, the seal 60 is a piston ring 160 (illustrated here for simplicity). Depending on the direction in which the piston 130 moves at a given time, the piston ring 160 abuts against either the high-pressure side or the low-pressure side of the groove 156, thereby sealing the leak path L.

[0045] In a conventional seal unit equipped with a piston ring 160, the dynamic pressure component is reduced at the first seal 60, starting from the high-pressure side H, and the static pressure component is reduced at the last seal 60. To avoid this, three bypasses 70a, 70b, and 70c are provided in addition to the leakage path L. Each bypass 70a, 70b, and 70c fluidly connects two immediately adjacent chambers 50 to each other.

[0046] Each bypass 70a, 70b, and 70c has one hole 72 extending parallel to the main axis X. In the illustrated embodiment, the bypasses 70a, 70b, and 70c pass through the projection 154, that is, from the first axial surface 182 of the piston disk 140 to the second axial surface 184 of the piston disk 140 located on the opposite side. Thus, each hole 72 connects two adjacent chambers 50 to each other. The holes 72 actually have a smaller diameter and are shown enlarged here. Each piston disk 140 further has an outer radial surface 186.

[0047] Bypasses 70a, 70b, and 70c provide a means for the gas arriving from the high-pressure side to flow into the next chamber 50 each time, in addition to the leakage path L. In this way, the pressure difference between the high-pressure side H and the low-pressure side N is reduced gradually and uniformly overall.

[0048] In the embodiment partially shown in Figure 2, the piston 130 has an integrated piston body 150. In this case as well, the piston body 150 has a cylindrical core 152 and a plurality of annular projections 154 that surround and extend around the core 152 in the circumferential direction. The configuration of the sleeve 20, piston rod 230, and seal 60 is the same as in the embodiment shown in Figure 1.

[0049] Bypasses 70a, 70b, and 70c are also formed by holes 72 in the embodiment shown in Figure 2. However, the holes 72 do not extend parallel to the main axis X. Rather, the holes 72 extend along a linear path from the bottom of groove 156 to the bottom of adjacent groove 156. The holes 72 extend completely through the core 152 of the piston body 150. In this case, the holes intersect with the main axis X. In other words, adjacent chambers 50 are connected to each other by holes 72 in this embodiment as well, thereby ensuring uniform pressure distribution across all seals 60.

[0050] The compressor 10, partially shown in Figure 3, has a packing casing 220 as a stationary part 20 and a piston rod 230 as a reciprocating part 30. The piston rod 230 reciprocates along the main axis X between the high-pressure side H and the low-pressure side N relative to the packing casing 220.

[0051] The packing casing 220 includes a disc body 40 consisting of multiple chamber discs 240, namely one base plate 222, multiple main chamber discs 223, one cover plate 224, and one end plate 226, which are arranged in contact with each other along the main axis X in this order. Each chamber disc 240 has one central hole. A piston rod 230 extends through the central hole. Each pair of adjacent chamber discs 240 together form a single groove 228, which opens radially inward.

[0052] The groove 228 of the chamber disc 240 is partially closed by the piston rod 230. In this way, the chamber disc 240 and the piston rod 230 form a plurality of chambers 50 that extend annularly around the main axis, arranged sequentially in the axial direction, with a leakage path L remaining between the chamber disc 240 and the piston rod 230.

[0053] Each chamber disk 240 has a first axial surface 282, a second axial surface 284 located on the opposite side of the chamber disk 240, and an inner radial surface 286 (see Figure 3A).

[0054] Four of the chambers 50 each contain one seal 60. Each seal 60 has a support ring 262, a seal ring 264, and a cover ring 266 (see Figure 3A). The seal ring 264 and the cover ring 266 are held to the piston rod 230 by a girder spring 270. In another embodiment, the seal 60 is configured differently and may have some rings. The support ring 262, when used as specified, does not contact the piston rod 230 and is positioned radially away from the piston rod 230. The pressure coming from the high-pressure side H presses the seal 60 against the chamber disk 240 which is closer to the low-pressure side N. The support ring 262 supports the seal 60 axially against the chamber disk 240.

[0055] The seal ring 264 contacts the piston rod 230 and thereby seals the leak path L; in other words, the seal ring 264 completely or partially closes the leak path L.

[0056] In addition to the leakage path L, four bypasses 70a, 70b, 70c, and 70d are provided, each fluidly connecting two adjacent chambers 50 (see Figure 3). The bypasses 70a, 70b, 70c, and 70d are formed by holes 72 (see Figure 3A). The holes 72 extend between the first axial surface 282 and the inner radial surface 286, thereby connecting adjacent chambers 50.

[0057] Within the hole 72 are arranged one restrictor 74 in the form of a screw-in member with a perforated plate 76, which is screwed into the hole 72. The perforated plate 76 has holes that define the minimum cross-section of each bypass 70a, 70b, 70c, and 70d. The holes in the perforated plate 76 of bypasses 70a, 70b, 70c, and 70d have diameters of 0.4 mm, 0.4 mm, 0.5 mm, and 0.6 mm, respectively, from the high-pressure side H. In other words, the minimum cross-sections of bypasses 70a, 70b, 70c, and 70d always decrease or remain unchanged toward the high-pressure side H.

[0058] The support ring 262 shown in Figure 4 can be used, for example, in the packing casing 220 shown in Figure 3. The support ring 262 has a first axial end face 272, a second axial end face 274 located on the opposite side, a radial inner surface 276, and a radial outer surface 278.

[0059] The support ring 262 further has a bypass 70 in the form of a hole 72. The hole 72 extends radially from the radial inner surface 276 to the radial outer surface 278. When used as specified, the support ring 262 does not contact the piston rod 230 with its radial inner surface 276 as described above. The support ring 262 also does not contact the packing casing 220 with its radial outer surface 278. In this way, the bypass 70 of the support ring 262 also connects the two adjacent chambers 50 (see Figure 3A).

[0060] Figure 5 partially shows a compressor 10 that is partially the same as the compressor 10 shown in Figure 3. This compressor 10 has a packing casing 220 as a stationary part 20 and a piston rod 230 as a reciprocating part 30. The piston rod 230 reciprocates along the main axis X between the high-pressure side H and the low-pressure side N relative to the packing casing 220.

[0061] The packing casing 220 includes a disc body 40 consisting of multiple chamber discs 240, namely one base plate 222, multiple main chamber discs 223, one cover plate 224, and one end plate 226, which are arranged in contact with each other along the main axis X in this order. Each chamber disc 240 has one central hole. A piston rod 230 extends through the central hole. Each pair of adjacent chamber discs 240 together form a single groove 228, which opens radially inward.

[0062] The groove 228 of the chamber disc 240 is partially closed by the piston rod 230. In this way, the chamber disc 240 and the piston rod 230 form a plurality of chambers 50 that extend annularly around the main axis, arranged sequentially in the axial direction, with a leakage path L remaining between the chamber disc 240 and the piston rod 230.

[0063] Each chamber disk 240 has a first axial surface 282, a second axial surface 284 located on the opposite side of the chamber disk 240, and an inner radial surface 286.

[0064] Four of the chambers 50 are each fitted with one seal 60. Each seal 60 has a support ring 262, a seal ring 264, and a cover ring 266 (see Figure 3A). The seal ring 264 and the cover ring 266 are held to the piston rod 230 by a girder spring 270. In another embodiment, the seal 60 is configured differently and may have some rings. The support ring 262, when used as specified, does not contact the piston rod 230 and is positioned radially away from the piston rod 230. The pressure coming from the high-pressure side H presses the seal 60 against the first axial surface 282 of the chamber disk 240. This causes the first axial surface 282 to form a seal surface 288. The support ring 262 supports the seal 60 axially to the chamber disk 240.

[0065] The seal ring 264 contacts the piston rod 230 and thereby seals the leak path L; in other words, the seal ring 264 completely or partially closes the leak path L.

[0066] A bypass 70 in the form of a groove 78 is provided in the region of the leakage path L, and the groove 78 fluidly connects two adjacent chambers 50 to each other. The groove 78 extends to a first axial surface 282, which is also the sealing surface 288. In this case, the groove 78 extends radially, completely penetrating the sealing surface 288. Even when the seal 60 is in full contact with the sealing surface 288, the groove 78 remains open in this way, forming the bypass 70.

[0067] The disk body 40 shown in Figure 6 is a chamber disk 240 for a compressor (not shown in detail). This chamber disk 240 is configured in the same way as the chamber disk 240 shown in Figure 5.

[0068] The chamber disc 240 has a central hole surrounded by an inner radial surface 286. The chamber disc 240 further has a first axial surface 282, which is also a sealing surface 288 for a seal (not shown). When used as specified, the seal contacts the sealing surface 288.

[0069] The sealing surface 288 is located on the axial projection of the chamber disk 240. The axial projection has an outer radial surface 186.

[0070] The chamber disc 240 has a bypass 70 in the form of a groove 78. The groove 78 extends from the outer radial surface 186 to the inner radial surface 286. When the seal is in contact with the sealing surface 288, the gas can continue to flow alongside the seal through the bypass 70. The size of the bypass 70 is predetermined so that appropriate leakage is achieved.

[0071] The groove 78 extends radially, that is, perpendicular to the main axis of the chamber disk 240. [Explanation of symbols]

[0072] 10 Compressor 20 Stationary part 30 Reciprocating part 40 discs 50 Chambers 60 stickers 70 Bypass 70a Bypass 70b Bypass 70c Bypass 70d Bypass 72 holes 74 aperture 76 Perforated plate 78 Groove 120 sleeves 122 Sliding surface 130 pistons 132 Base Plate 140 Piston Disc 150 piston bodies 152 cores 154 Protrusion 156 Groove 160 Piston Rings 182 First axial direction surface 184 Second axial direction surface 186 Outer radial plane 220 Packing casing 222 Base Plate 223 Main Chamber Disk 224 Cover Plate 226 End Plate 228 Groove 230 Piston Rod 240 Chamber Discs 262 Support ring 264 Seal Ring 266 Covering 270 Garter spring 272 First axial end face 274 Second axial end face 276 Radial inner surface 278 Radial outer surface 282 First axial direction surface 284 Second axial direction surface 286 Inner radial plane 288 sealing surface H High-voltage side N Low pressure side L Leakage Path X main axis

Claims

1. A compressor (10) comprising a stationary part (20), a part (30) that reciprocates along a main axis (X), and a leakage path (L) extending in the axial direction between the stationary part (20) and the reciprocating part (30), Between the stationary portion (20) and the reciprocating portion (30), a plurality of chambers (50) are defined, which are arranged sequentially in the axial direction and extend in an annular manner around the main axis (X). In a compressor (10) in which a seal (60) for closing or reducing the leak path (L) is located inside at least one of the chambers (50), At least one bypass (70, 70a, 70b, 70c, 70d) is provided to fluidly connect the two chambers (50) to each other. Multiple bypasses (70, 70a, 70b, 70c, 70d) are provided, and of each pair of adjacent bypasses (70, 70a, 70b, 70c, 70d), the bypass (70, 70a, 70b, 70c, 70d) located closer to the high-pressure side (H) of the compressor (10) has a smaller minimum cross-sectional area M than the bypass (70, 70a, 70b, 70c, 70d) located closer to the low-pressure side (N) of the compressor (10). The bypasses (70, 70a, 70b, 70c, 70d) are provided in the stationary portion (20) or the reciprocating portion (30) of the compressor (10).

2. A compressor (10) comprising a stationary portion (20), a portion (30) that reciprocates along a main axis (X), and a leakage path (L) extending in the axial direction between the stationary portion (20) and the reciprocating portion (30), Between the stationary portion (20) and the reciprocating portion (30), a plurality of chambers (50) are defined, which are arranged sequentially in the axial direction and extend in an annular manner around the main axis (X). In a compressor (10) in which a seal (60) for closing or reducing the leak path (L) is located inside at least one of the chambers (50), At least one bypass (70, 70a, 70b, 70c, 70d) is provided to fluidly connect the two chambers (50) to each other. Multiple bypasses (70, 70a, 70b, 70c, 70d) are provided, and of each pair of adjacent bypasses (70, 70a, 70b, 70c, 70d), the bypass (70, 70a, 70b, 70c, 70d) located closer to the high-pressure side (H) of the compressor (10) has a smaller minimum cross-sectional area M than the bypass (70, 70a, 70b, 70c, 70d) located closer to the low-pressure side (N) of the compressor (10). The aforementioned bypasses (70, 70a, 70b, 70c, 70d) are provided in addition to the aforementioned leak path (L) and are located in the compressor (10).

3. The compressor (10) according to claim 1 or 2, wherein the stationary portion (20) is a sleeve (120) and the reciprocating portion (30) is a piston (130), or the stationary portion (20) is a packing casing (220) and the reciprocating portion (30) is a piston rod (230).

4. The compressor (10) according to any one of claims 1 to 3, wherein the bypasses (70, 70a, 70b, 70c, 70d) fluidly connect two immediately adjacent chambers (50) to each other.

5. The aforementioned bypasses (70, 70a, 70b, 70c, 70d) are 2 mm ２ A compressor (10) according to any one of claims 1 to 4, having a minimum cross-sectional area M less than or equal to.

6. The compressor (10) according to any one of claims 1 to 5, wherein the bypass (70, 70a, 70b, 70c, 70d) is formed by at least one hole (72).

7. The compressor (10) according to claim 6, referencing claim 3, wherein the piston (130) or the packing casing (220) has a plurality of disc bodies (40) arranged sequentially in the axial direction, the disc body (40) having a first axial surface (182, 282), a second axial surface (184, 284) arranged on the opposite side with respect to the disc body (40), and a radial surface (186, 286), and 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).

8. The compressor (10) according to claim 6 or 7, wherein the hole (72) extends at least partially parallel to the main axis (X).

9. The compressor (10) according to any one of claims 6 to 8, referencing claim 3, wherein the piston (130) has a cylindrical core (152) and a plurality of annular projections (154) that surround and extend around the core (152) in the circumferential direction, and the hole (72) extends at least partially through the core (152).

10. The compressor (10) according to claim 3, which references claim 1, or any one of claims 4 to 5, which references claim 1 and claim 3, wherein the bypasses (70, 70a, 70b, 70c, 70d) are provided in the region of the leakage path (L).

11. The compressor (10) according to claim 10, wherein the bypasses (70, 70a, 70b, 70c, 70d) are grooves (78).

12. The compressor (10) according to claim 11, wherein the piston (130) or the packing casing (220) has a plurality of disc bodies (40) arranged sequentially in the axial direction, the disc bodies (40) have a sealing surface (288), and the groove (78) extends within the sealing surface (288).

13. A compressor (10) according to any one of claims 6 to 9, referencing claim 3, wherein a throttling (74) that defines the minimum cross-sectional area M of the bypass (70, 70a, 70b, 70c, 70d) is arranged in the hole (72) or groove (78).

14. The compressor (10) according to claim 13, wherein the throttling (74) is a screw-in member having a perforated plate (76) screwed into the hole (72), or an insertion member having a perforated plate (76) inserted into the groove (78).

15. The compressor (10) according to claim 13 or 14, wherein the throttling (74) includes a porous material.

16. A disk body (40) formed for use in a compressor (10) according to any one of claims 1 to 14, comprising a first axial surface (182, 282), a second axial surface (184, 284) located on the opposite side of the disk body (40), and a radial surface (186, 286), A disk body (40) characterized by bypasses (70, 70a, 70b, 70c, 70d) extending 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).

17. The disk body (40) according to claim 16, wherein the radial surfaces (186, 286) are the inner radial surface (286) or the outer radial surface (186).

18. A seal (60) formed for use in a compressor (10) according to any one of claims 1 to 14, comprising a first axial end face (272), a second axial end face (274), a radial inner surface (276), and a radial outer surface (278), A seal (60) characterized by bypasses (70, 70a, 70b, 70c, 70d) extending between at least two of the aforementioned surfaces (272, 274, 276, 278).

19. Use of a disk body (40) according to any one of claims 16 to 17 or a seal (60) according to claim 18 in a compressor (10).

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