• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    COMPRESSOR. A sealing system is equipped with a dry gas seal 15 having a swivel ring 16 positioned between a casing 11a and a rotor shaft 11 and, around the circumference of the rotor shaft 11, and with stationary rings 19,20 provided on the casings 1a containing elastic members 17,18 interpositioned therebetween so as to be able to contact the octagonal edge surfaces of the swivel ring 16 which are substantially octagonal to the axis of the rotor 11; a sealing gas channel 6 having one end connected with a discharge channel 5, and the other end connected so as to connect to a space 37 present between the envelope 1a and the outer peripheral surface 16a of the swivel ring 16 in the dry seal of gas 15, and having a duct gas regulating valve 8 provided therein; and a duct gas channel 26 having one end connected to connect with space 37 via a hole and passage 35 formed in the housing 1a of the swivel ring 16, with the other end connected with an inlet channel 3.
    公开号:BR112013009472B1
    申请号:R112013009472-9
    申请日:2011-10-11
    公开日:2021-05-18
    发明作者:Toshiki Kitano；Yasushi Amano
    申请人:Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel, Ltd；
    IPC主号:
    专利说明:

    Technical Field
    [001] The invention is related to a compressor, referring more specifically to a compressor making use of the so-called dry gas seal. Technical Fundamentals
    [002] Although several types of compressors are known, most of them consist of a type rotating a rotational body, such as an impeller, helical rotor, spiral rotor, vane type for axial flow and similar elements and compressible fluid accompanying the rotation of the rotational body. Consequently, in the compressor, a compression space is formed for the accommodation of the main section of the rotational body and for the compression of fluid, and with the formation of a bearing section to provide support to an axis of the rotational body. In addition, in the gap between the compression space and the bearing section and in the gap between the compression space and the atmospheric space, various seals are used in order to prevent compressed fluid leakage from the compression space and for the flow of a lubricant (oil, grease, and the like) and air and the like (particularly in a compressor and the like making use of the so-called processing gas in the form of a fluid to be compressed) to from the bearing section to the compression space.
    [003] Particularly, with respect to the compressor that handles flammable gas and explosive gas, such as hydrocarbon and such elements, toxic gas, corrosive gas and such elements as the fluid to be compressed, the constitution of the seal for gas becomes a factor of importance. Currently, the so-called dry gas seal draws attention as the dry seal does not require any use of oil as the sealing material.
    [004] In general terms, the dry gas seal consists of a rotating ring integrally rotating along an axis of the rotational body and stationary rings arranged in positions opposite the rotational ring along the surfaces of vertical edges, generally orthogonal to the axis and attached to the wrapping and similar elements via an elastic material. In the dry gas seal, in the state in which the rotational body stops, the stationary rings are confined in front of the rotating ring, the sealing surfaces being formed, and preventing the outflow and gas-like elements to be tablet. Furthermore, on most of the vertical edge surfaces of the rotating ring of the dry gas seal, basically the surfaces opposite the stationary rings, spiral grooves are formed. Furthermore, in the state where the rotating body is rotating, the sealing gas flows into the spiral grooves, with the formation of a dynamic pressure, and the formation of narrow gaps between the rotating ring and the stationary rings, with the sealing surfaces for the sealing gas being formed therein, and further preventing the outflow of gas-like elements to be compressed.
    [005] In Patent Document No. 1 (JP-A No. 2010-121463), there is a presentation of an example of sealing a compressor by means of dry gas sealing. As shown in Fig. 9, the seal of Patent Document No. 1 includes a dry gas seal section 104 and a dam seal section 105 between a compressor casing 102 at the rear of an impeller 102 and a shaft of impeller rotor 103. The dry gas seal section 104 includes a stationary side dry gas seal body 106 secured to the compressor housing 102 and a rotatable side gas seal body 107 secured to the impeller rotor shaft 103. In addition, the dry gas seal section 104 is formed from a primary dry gas seal section 108 and a secondary dry gas seal section 109. In the primary dry gas seal section 108 and in the dry gas seal secondary section 109, the swivel rings 110A, 110B attached to the dry gas seal body on the swivel side 107 and the stationary rings 112, 112B attached to the dry gas seal body on the stationary side 106 via the springs 11A, 11B are respectively positioned to be opposite each other in the axial direction. On the surfaces of the swivel rings 110A, 110B opposite the stationary rings 112A, 112B, spiral grooves, not shown, are formed. The boom seal section 105 is secured to the compressor housing 102 and is integrally connected with the dry gas seal body on the stationary side 106.
    [006] According to the seal described in Patent Document No. 1, even when a buoyant force acting on an operation at high pressure becomes large, the seal can withstand the buoyancy as a function of resistance, and it can be guaranteed the stability of the rotational body.
    [007] In addition, when the liquid (drainage and the like) infiltrates along the sealing surface formed by the dry gas seal, the dynamic pressure formed becomes unstable, and the gap is not formed with stability between the rotating ring and the stationary rings. This phenomenon is considered to originate from the variation that occurs in the force (floating force) generated between the rotating ring and the stationary rings due to the coexistence of non-compressible liquid and compression gas on the sealing surfaces. Therefore, when liquid infiltrates along the sealing surfaces, the rotating ring and the stationary rings are brought into contact with each other, and the sealing surfaces can very possibly get damaged during rotation of the rotational body. Invention Summary Technical problems
    [008] The purpose of the present invention is to provide a compressor equipped with a sealing system capable of suppressing the occurrence of failures arising from the infiltration of liquid together with a dry gas seal and with the liquefaction of supplied sealing gas in a compressor employing dry gas seal as a seal. Problem Solving
    [009] As a mechanism for solving the problems, the compressor of the present invention comprises a compressor that includes a compressor body incorporating a compression space for accommodating a rotor arranged so that the rotor shaft is generally horizontal, a casing being provided containing an inlet nozzle and an outlet outlet communicating with the compression space, an inlet channel connected with the compressor body inlet outlet, and an outlet channel connected with the outlet discharge from the compressor body, with the fluid being sucked from the inlet channel through the inlet port, and the fluid being compressed in the compression space and discharged to the discharge channel via the discharge port, where the compressor includes a dry gas seal positioned between the casing and the rotor shaft and having a swivel ring disposed around the circumference of the rotor shaft and the rings. stationary are provided in the casing containing elastic components interposed between them, so as to be able to confine themselves around the surfaces of orthogonal edges of the rotating ring that are substantially orthogonal to the rotor axis, a sealing gas channel having one end connected with the discharge channel, with the other end connected so as to communicate with a space present between the outer peripheral surface of the swivel ring in the dry gas seal and the housing, and having provision for a gas regulating valve sealing, and a gas conduit channel having one end connected to communicate with the space via a through hole in the housing below the swivel ring, and the other end connected to the inlet channel.
    [010] According to this constitution, even when liquid such as that of conduit and related elements infiltrates together with the sealing gas, or even when liquefaction of the sealing gas of the supplied liquid occurs, the liquid may be rapidly discharged towards the inlet channel together with the sealing gas through the gas flow channel without allowing the liquid to remain on the sealed surfaces between the rotating ring and the stationary rings formed in the dry gas seal. Consequently, one can prevent the occurrence of failures arising from the infiltration of liquid with the dry gas seal and the liquefaction of the supplied seal gas.
    [011] It is preferred that the orifice is provided in the gas flow channel. According to this constitution, the compressed fluid and the liquid (from conduit and the like) can be returned to the inlet channel, little by little, while preserving the temperature of the sealing gas channel and the gas flow channel . Furthermore, in particular, when using the compressor under a high pressure differential condition with a comparatively smaller consumption amount of the process gas consisting of the fluid compressed in the dry gas seal (a situation where the pressure differential between the sealing gas supply pressure consisting of a part of the fluid compressed in the sealing gas channel and the pressure on the side of the sealing gas being discharged comprises a high pressure), a search for the regulating valve may possibly occur of sealing gas. However, by allowing the process gas and fluid in an appropriate amount to flow through the orifice, the selection of the regulator valve for the sealing gas can be facilitated.
    [012] It is preferred that the flow regulating valve is provided in the gas flow channel. According to this constitution, the flow rate of the gas flow channel can be adjusted to the stroke of a wide range, and the selection of the sealing gas regulating valve can be further facilitated. Furthermore, even when using a gas with a change in molecular weight and pressure, the return amount of gas along the inlet side can be maintained to represent an optimized amount.
    [013] It is preferred that there is provision for an emergency channel having one end connected with the inlet channel and the other end connected with the sealing gas channel via a check valve. According to this constitution, even when a defect following the inlet pressure of the sealing gas regulator valve arises from a sudden fluctuation occurring in the inlet pressure, the pressure of the sealing gas channel is maintained, at least , in the inlet pressure due to the provision of the emergency channel. Therefore, the state can be prevented from occurring as the "back pressure condition", basically the state of "seal gas channel pressure < than the inlet pressure at the inlet port". Consequently, a state of an appropriate pressure (minimum required pressure) can be maintained by being applied to the dry gas seal, eliminating the possibility of damage occurring.
    [014] It is preferred that a shut-off valve is provided in the emergency channel. According to this constitution, it can be prevented by opening the shut-off valve in the operation of the compressor and closing the shut-off valve to stop the infiltration of a foreign object and liquid in the sealing gas channel and consequently next to the wrap interior at the stop.
    [015] It is preferred that a sealing gas supply source providing sealing gas is connected to the sealing gas channel. According to this constitution, the sealing gas can be safely supplied from the sealing gas supply source close to the sealing gas channel. Consequently, a constitution can be arrived at including an emergency channel. Advantageous Effects of the Invention
    [016] According to the present invention, even when the liquid, such as the conduit and the like, infiltrates together with the sealing gas, or even when the liquefaction of the sealing gas of the supplied liquid occurs, the liquid can be quickly discharged towards the inlet channel together with the sealing gas through the gas flow channel without allowing the liquid to remain on the sealing surfaces between the rotating ring and the stationary rings formed in the dry gas seal. Consequently, it is possible to eliminate the occurrence of failures arising from the infiltration of liquid together with the dry gas seal and the liquefaction of the supplied seal gas. Brief Description of Drawings
    [017] Fig. 1 comprises a schematic drawing showing a compressor of a first embodiment of the present invention.
    [018] Fig. 2 consists of an enlarged view of a compressor sealing section related to the first embodiment of the present invention.
    [019] Fig. 3 consists of a drawing showing an orthogonal edge surface of the rotating ring.
    [020] Fig. 4 comprises a schematic drawing showing a compressor of a second embodiment of the present invention.
    [021] Fig. 5 consists of an enlarged view of a compressor sealing section related to the second embodiment of the present invention.
    [022] Fig. 6 consists of a drawing showing a modification of the sealing section.
    [023] Fig. 7 consists of a drawing showing a modification of the present invention.
    [024] Fig. 8 consists of a drawing showing a modification of the present invention.
    [025] Fig. 9 consists of an enlarged view of a compressor sealing section coming according to the prior art. Description of Modalities
    [026] Fig. 1 shows a compressor of the first embodiment of the present invention. The compressor related to the present invention includes a compressor body 1 in which a rotational body (rotor) (not shown) is accommodated in a compression space (not shown) formed in an envelope 1a.
    [027] An inlet channel 3 is connected next to the inlet port 2 of the compressor body 1. In addition, an outlet channel 5 is connected next to the discharge port 4 of the compressor body 1.
    [028] The compressor body 1 sucks the liquid to be compressed, for example, in so-called process gas from the inlet nozzle 2 through the inlet channel 3. In addition, the compression body 1 compresses the process gas in the compression space described above, discharging it later from the discharge nozzle 4, and supplying it for supply at a destination, not illustrated, through the discharge channel 5.
    [029] In addition, there is the provision of a gas seal channel 6 containing one end connected to the discharge channel 5 and the other end connected to a dry gas seal 15 described below. Through the sealing gas channel 6, a part of the process gas after compression is supplied together with the sealing gas regulating valve 8 in the form of sealing gas. In addition, the sealing gas regulating valve 8 has functions relating to gas pressure in space 38 described below with a reference pressure section 27 described below and supplying sealing gas having a sealing gas pressure higher than the gas pressure.
    [030] In the sealing gas channel 6, there is provision for a filter 7, the sealing gas regulating valve 8, a check valve 9 so as to form a branch point of the discharge channel 5.
    [031] The filter 7 captures the impure matter mixed in the process gas moving through the seal gas channel 6 and purifying the process gas. The seal gas regulating valve 8 regulates the flow rate of the process gas to a predetermined value so that a portion of the process gas is bypassed as the seal gas. The check valve 9 assumes the role of only allowing the flow of the process gas directed from the branch point of the sealing gas channel 6 and the discharge channel 5 towards the dry gas seal 15, and preventing the occurrence of a reverse flow of the sealing gas.
    [032] A rotor shaft 11 consisting of a rotational body shaft (rotor) constituting the compressor body 1 penetrates the inlet side of the envelope 1a constituting the compressor body 1, being connected to the shaft of a transmission component 12 ( transmission machine) and to a transmission shaft 14 via a coupling 13. In addition, the dry gas seal 15 is positioned around the rotor shaft 11 so as to effect the seal between the casing 1a and the rotor shaft 11 .
    [033] Fig. 2 shows the details of the dry gas seal 15. The dry gas seal 15 includes a rotating ring 16 integrally rotating with the rotor shaft 11 and the stationary rings 19, 20 fixed together with the envelope 1a via the elastic components 17, 18 on both sides of the swivel ring 16. As shown in Fig. 3, on the orthogonal edge surfaces of the swivel ring 16 of the dry gas seal 15, basically the opposing surfaces of the stationary rings 19, 20, come to be spiral grooves 33 are formed. Spiral groove 33 is formed so as to approach the central side as it travels from the outer periphery of the swivel ring 16 in the opposite direction to the direction of rotation, and the end portion of the it is located between the outer periphery and the inner periphery. The spiral grooves 33 being open near an outer peripheral surface 16a of the swivel ring 16. The stationary rings 19, 20 are arranged to be able to abut against the orthogonal edge surfaces of the swivel ring 16, generally orthogonal to the axis of rotor 11 by the elastic components 17, 18.
    [034] In addition, around a part of the constitution of the dry gas seal 15 along the side of the transmission member 12 (transmission machine), the stationary ring 20, basically the rotor shaft 11 on the side of the atmospheric air, sealing components 22, 23, such as labyrinth seals and the like are positioned between casing 1a and rotor shaft 11.
    [035] Furthermore, in a space between the sealing component 22 and the sealing component 23, there is a connection of a nitrogen supply channel 24 in order to be able to supply nitrogen from a supply source of nitrogen. In the nitrogen supply channel 24, a flow regulating valve 25 is interposed so as to regulate the flow rate of nitrogen flowing through it to a predetermined value.
    [036] In addition, the compressor related to the present invention includes a gas flow channel 26 and the reference pressure section 27.
    [037] With respect to the gas flow channel 26, one end is connected in order to communicate with a space 37 present between the outer peripheral surface 16a of the swivel ring 16 and the envelope 1a through a through hole 35 formed in the envelope 1a below the swivel ring 16, with the other end being connected to the inlet channel 3. In the gas flow channel 26, a check valve 28 is interpositioned, allowing only directed flow towards the side of the inlet channel 3 coming from the dry gas seal side 15 and an orifice. Orifice 29 is disposed on the downstream side of check valve 28.
    [038] The reference pressure section 27 is positioned on the envelope 1a so as to communicate with the space 38 present between the envelope 1a on the side of the compression space of the dry gas seal 15 and the rotor shaft 11. Once that the space 38 communicates with the inlet nozzle 2 on the inside of the compressor body 1, its pressure is equalized with the inlet pressure. Therefore, it is configured that the pressure on the side of the compression space of the envelope 1a can be referenced via the reference pressure section 27. The reference pressure section 27 is connected together with the sealing gas regulating valve 8 via channels. Consequently, it is configured that the opening of the sealing gas regulating valve 8 can be regulated depending on the pressure existing in the reference pressure section 27, basically, the pressure on the side of the compression space of the envelope 1a.
    [039] Next, there is a description of the action of the compressor provided with the dry gas seal 15 constituted according to the previous description. In the state in which the rotor shaft 11 representing the rotational body comes to a stop, in the dry gas seal 15, the stationary rings 19, 20 abut on the rotating ring 16 by means of springs 17, 18 (elastic components), forming sealing surfaces, and preventing outflow and the like of the gas to be compressed along the side of the transmission component 12 (transmission machine), basically, the side of atmospheric air, from the side of the compressor body 1 (side of the compression space).
    [040] On the other hand, in the state in which the rotor shaft 11 is rotating, the sealing gas flows into the space 37 between the outer peripheral surface 16a of the swivel ring 16 and the envelope 1a via a through hole 36 of the wrap 1a. Furthermore, the sealing gas spreads from an opening section of the outer peripheral surface 16a of the swivel ring 16 into the spiral grooves 33. In addition, there is the formation of dynamic pressure, with narrow intervals coming to be formed between the swivel ring 16 and the stationary rings 10, 20, with the sealing surfaces in the sealing gas being constituted there, preventing outflow and the like of the gas to be compressed along the side of the transmission component 12 (transmission machine), basically, the atmospheric air side, from the side of the compressor body 1 in a similar way.
    [041] The process gas having been supplied to the dry gas seal 15 via the seal gas channel 6 passes through the narrow gap between the rotating ring 16 and the stationary ring 20 in the form of seal gas, coming to be subsequently discharged towards continuous combustion through a discharge channel 21 on the side of the atmospheric air having a lower pressure than the side of the compression space.
    [042] Furthermore, when the process gas supplied to the dry gas seal 15 moves on the compression space side, the process gas returns to the compression space, being compressed along with the process gas having been sucked through the 2 inlet mouthpiece.
    [043] Having supplied nitrogen to the space between the sealing component 22 and the sealing component 23, through the nitrogen supply channel 24, it passes through a narrow gap between the sealing component 22 and the rotor shaft 11 or by a narrow gap between sealing member 23 and rotor shaft 11. From there, nitrogen acts as the sealing gas. Furthermore, the nitrogen having reached the discharge channel 21 through the narrow gap present between the sealing member 22 and the rotor shaft 11, it is discharged towards continuous combustion through the discharge channel 21. nitrogen having exited through the narrow gap between the sealing member 23 and the rotor shaft 11 is now discharged into atmospheric air as is.
    [044] Even when liquid such as conduit and such elements infiltrate the sealing gas, or even when liquefaction of the sealing gas of the supplied liquid occurs, the liquid can be quickly discharged towards the ingress 3 together with the sealing gas through the gas flow channel 26 without the possibility of liquid remaining on the sealing surfaces between the swivel ring 16 and the stationary rings 19, 20 formed in the dry gas seal 15. if it comes to eliminate the occurrence of failures arising from the infiltration of liquid together with the dry gas seal 15 and the liquefaction of the supplied sealing gas. Furthermore, in the case of sealing gas, particularly when the process gas is diverted to the sealing gas in accordance with the present modality, the inclusion of those (liquefied) parts pertinent to the duct very often occurs following the change in temperature ,pressure and gender elements. Even in such a condition, according to the present invention, the failures arising from the liquefaction of the sealing gas can be eliminated according to the above description.
    [045] In addition, through the interposition of the orifice 20 in the gas flow channel 26, the processing gas and the liquid (duct and the like) can be returned to the inlet channel 3, little by little, while the pressure of the sealing gas channel 6 and the gas flow channel 26 being maintained. Furthermore, in particular, when the compressor is used under a situation where the high pressure differential with a comparatively lower amount of consumption of the process gas (a situation in which the pressure differential between the sealing gas supply pressure in the sealing gas channel 6 and the pressure on the sealing gas side comes to be discharged, comprising of the high pressure), the search for seal gas regulating valve 8 could possibly occur. However, by having the process gas and liquid in appropriate amounts flow out through orifice 29, selection of the sealing gas regulating valve 8 can be facilitated.
    [046] Fig. 4 and Fig. 5 show a compressor of the second embodiment of the present invention. In this compressor of the second mode, most of the constitutions are presented in common with those referring to the compressor of the first mode shown in Fig. 1 and Fig. 2, however, an emergency channel 31 becomes available in addition to the constitution of the first modality.
    [047] With respect to the emergency channel 31, one end of it is connected to the inlet channel 3, and the other end to the sealing gas channel 6 downstream of the check valve 9. In the emergency channel 31, it has - the interposition of a check valve 32 allowing only the flow directed from the side of the inlet channel 3 towards the side of the sealing gas channel 6.
    [048] When the pressure differential between the sealing gas supply pressure in the sealing gas channel 6 and the pressure on the sealing gas side comes to be discharged, it becomes high pressure, with the amount of part of the process gas being consumed as the sealing gas increases. So that the quantity does not increase excessively, the sealing gas regulating valve 8 regulates the supply pressure PS of the sealing gas (a part of the process gas after compression) in the sealing gas channel 6 downstream of the regulating valve of the sealing gas 8 so as to become the reference pressure (= inlet pressure) PI + α (eg approx 4 bar maximum) based on the pressure of the reference pressure section 27. However, when fluctuation occurs suddenly of the reference pressure PI (= inlet pressure) and there is no provision for an emergency channel 31, failure may occur following the inlet pressure PI of the sealing gas regulating valve 8, in a state under the presence of a condition of counter-pressure where there may be damage to the dry gas seal 15, namely a state in which the "supply pressure PS of the seal gas channel 6 < than the reference pressure PI (= pressure of in entrance) at the entrance mouth 2".
    [049] Under the "back pressure condition", the force generated between the swivel ring 16 and the stationary rings 10, 20 of the dry gas seal 15 (floating force) becomes insufficient, with the swivel ring 16 and the stationary rings 19, 20 being able to come into contact with each other during rotation of the rotational body 2, and with the sealing surfaces being damaged.
    [050] Through the provision of the emergency channel 31, even when a failure may occur following the reference pressure (= inlet pressure) of the sealing gas regulating valve 8 arising from a sudden fluctuation of the pressure of ingress, the pressure of the sealing gas channel 6 is maintained at least at the value in magnitude of the pressure identical to the inlet pressure, and therefore the "back pressure condition", namely, the state referring to "pressure of PI supply at the 2" inlet port can be avoided. As a result, a state may be maintained as to an appropriate pressure (minimum required pressure) applied to the dry gas seal 15, eliminating the possibility of damage occurring.
    [051] The present invention is not restricted to those modalities of reference, being possible several changes, according to the description below.
    [052] As shown in Fig. 6, the dry gas seal 15 can be provided with a swivel ring 30 being provided between the envelope 1a, from the position where the nitrogen supply channel 24 is connected, and the shaft of rotor 11 and with a stationary ring 40 being positioned with the rotating ring 39. In this way, the amount of nitrogen leakage from an existing gap between the envelope 1a and the rotor shaft 11 on the atmospheric air side can be reduced, and there may be a reduction in the amount of nitrogen consumed.
    [053] Instead of the interposition of the orifice 20 next to the gas flow channel 26, there may be the interpositioning of the flow rate regulating valve regulating the flow rate. According to this constitution, the flow rate of the gas flow channel 26 can be regulated to a wide range, and the selection of the sealing gas regulating valve 8 can be further facilitated. Furthermore, even when using gas with changes in molecular weight and pressure, the return amount of this gas along the inlet side can be preserved in order to have an optimized amount.
    [054] As shown in Fig. 7, a shut-off valve 42 can be interposed in the emergency channel 31 between the inlet channel 3 and the check valve 32. In addition, a filter 43 can be interposed in the emergency channel. between the shut-off valve 42 and the non-return valve 32. According to this constitution, by opening the shut-off valve 42 when operating the compressor, and by closing the shut-off valve 42 when stopping, it prevents the presence of a foreign object and liquid from infiltrating the sealing gas channel 16 and, consequently, going into the interior of the envelope 1a at the time of the stop.
    [055] As shown in Fig. 8, instead of having provision for an emergency channel 31 in the second mode compressor, a sealing gas supply source 45 supplying with nitrogen in the form of sealing gas can be connected with the sealing gas channel 6 via a check valve 44. According to this constitution, the sealing gas can be safely supplied from the sealing gas supply source 45 to the sealing gas channel 6. Consequently, a constitution of security regarding the emergency channel 31 can be obtained. In addition, it is also possible to provide both the sealing gas supply source 45 and the emergency channel 31. In this case, the sealing gas can be safely supplied from the sealing gas channel 6 to the 1st wrap.
    [056] Instead of connecting the reference pressure section 27 and the sealing gas regulating valve 8 to each other via a channel and directing the regulation of the opening of the sealing gas regulating valve 8, it can be configured that the pressure valve measured in the reference pressure section 27 will be transmitted to a control device (not shown) with the opening of the sealing gas regulating valve 8 being indirectly regulated via the control device.
    [057] The pressure in space 38 can be equalized with the inlet pressure through the external piping.
    [058] The swivel ring 16 was described by an example of a rotational direction containing only one direction, however, the swivel ring 16 is not restricted to this situation, a swivel ring being able to rotate in both directions can be used, where grooves having a sealing function under dry gas sealing mode come to be formed on the orthogonal edge surfaces.
    [059] The sealing gas regulating valve 8 can consist of a regulating valve of any type, such as a self-actuating regulating valve, an automatic regulating valve, and so on. In addition, in the mode described above, one is presented in which the filter 7, the sealing gas regulating valve 9, and the check valve 9 have been interposed in the sealing gas channel 6 so as to form the branch point of the discharge channel 5, however the present invention is not limited to this condition, and a differentiated order for the filter 7, the sealing gas regulating valve 8, and the check valve 9 may be acceptable. In addition, orifice 29 can be positioned on the upstream side of check valve 29. Reference Numeral List 1...compressor body 1a...envelope 2...inlet port 3...inlet channel 4...discharge port 5...discharge channel 6...seal gas channel 7...filter 8...seal gas regulating valve 9...check valve 11...shaft of rotor 12...transmission component (transmission machine) 13...coupling 14...transmission shaft 15...dry gas seal 16, 39...spinning ring 17, 18...spring ( elastic component) 19, 20, 40...stationary ring 21...discharge channel 22, 23...sealing component 24...nitrogen supply channel 25...flow regulating valve 26... gas flow channel 27...reference pressure section 28...check valve 29...orifice 31...emergency channel 32...check valve 33...slots 35...orifice passage 36...through hole 37...space 38...space 42...stop valve tion 43...filter 45...seal gas supply source
    权利要求:
    Claims (6)
    [0001]
    1. Compressor, CHARACTERIZED in that it comprises: a compressor body (1) including a compression space for accommodating a rotor arranged so that a rotor shaft (11) becomes generally horizontal and a casing (1a ) provided with an inlet mouthpiece (2) and an outlet mouthpiece (4) which communicate with the compression space; an inlet channel (3) connected to the inlet port (2) of the compressor body (1); and an discharge channel (5) connected to the discharge nozzle (4) of the compressor body (1); with the fluid being sucked from the inlet channel (3) through the inlet mouthpiece (2), and the fluid being compressed in the compression space and discharged into the discharge channel (5) via the discharge outlet (4), the compressor including: a dry gas seal (15) having a swivel ring (16, 39) positioned between the housing (1a) and the rotor shaft (11) and disposed about the circumference of the rotor shaft (11 ), and stationary rings (19, 20, 40) provided on the envelope (1a) with elastic components (17, 18) interposed between them so as to be able to confine themselves to the orthogonal edge surfaces of the swivel ring (16, 39 ) which are substantially orthogonal to the rotor shaft (11); a sealing gas channel (6) having one end connected to the discharge channel (5), the other end connected so as to communicate with a space (37) between an outer peripheral surface of the swivel ring (16, 39) at the dry gas seal (15) and the wrap (1a), and having a sealing gas regulator (8) provided therein; and a gas flow channel (26) having one end connected to communicate with the space (37) via a through hole (35) formed in the housing (1a) below the swivel ring (16, 39), and the other end connected to the inlet channel (3).
    [0002]
    2. Compressor according to claim 1, CHARACTERIZED by the fact that an orifice (29) is provided in the gas flow channel (26).
    [0003]
    3. Compressor according to claim 1, CHARACTERIZED by the fact that a flow regulating valve (25) is provided in the gas flow channel (26).
    [0004]
    4. Compressor according to claim 1, CHARACTERIZED by the fact that it further comprises an emergency channel (31) having one end connected to the inlet channel (3) and the other end connected to the sealing gas channel (6) via a check valve (32).
    [0005]
    5. Compressor according to claim 4, CHARACTERIZED by the fact that a shut-off valve (42) is provided in the emergency channel (31).
    [0006]
    6. Compressor according to claim 1, CHARACTERIZED by the fact that a sealing gas supply source (45) that supplies the sealing gas is connected to the sealing gas channel (6).
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    JPWO2019111661A1|2020-11-19|Liquid supply type screw compressor
    同族专利:
    公开号 | 公开日
    JP5231611B2|2013-07-10|
    EP2631489B1|2018-09-26|
    CN103168174A|2013-06-19|
    US9239061B2|2016-01-19|
    CN103168174B|2015-09-30|
    JP2012107609A|2012-06-07|
    BR112013009472A2|2020-06-16|
    EP2631489A1|2013-08-28|
    EP2631489A4|2017-10-18|
    US20130195649A1|2013-08-01|
    WO2012053389A1|2012-04-26|
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    法律状态:
    2020-06-30| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2020-07-14| B06U| Preliminary requirement: requests with searches performed by other patent offices: procedure suspended [chapter 6.21 patent gazette]|
    2021-04-06| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2021-05-18| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 11/10/2011, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    JP2010237547|2010-10-22|
    JP2010-237547|2010-10-22|
    JP2011-159087|2011-07-20|
    JP2011159087A|JP5231611B2|2010-10-22|2011-07-20|Compressor|
    PCT/JP2011/073311|WO2012053389A1|2010-10-22|2011-10-11|Compressor|
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