EP3859158A1 - Compressor device - Google Patents

Compressor device Download PDF

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Publication number
EP3859158A1
EP3859158A1 EP21164419.0A EP21164419A EP3859158A1 EP 3859158 A1 EP3859158 A1 EP 3859158A1 EP 21164419 A EP21164419 A EP 21164419A EP 3859158 A1 EP3859158 A1 EP 3859158A1
Authority
EP
European Patent Office
Prior art keywords
compressor
channel
inlet
passive element
compressors
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP21164419.0A
Other languages
German (de)
English (en)
French (fr)
Inventor
Stefan Paul M. DE KERPEL
Jan Achiel L STOFFIJN
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Atlas Copco Airpower NV
Original Assignee
Atlas Copco Airpower NV
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Atlas Copco Airpower NV filed Critical Atlas Copco Airpower NV
Publication of EP3859158A1 publication Critical patent/EP3859158A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/123—Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B41/00—Pumping installations or systems specially adapted for elastic fluids
    • F04B41/06—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F5/00—Jet pumps, i.e. devices in which flow is induced by pressure drop caused by velocity of another fluid flow
    • F04F5/44—Component parts, details, or accessories not provided for in, or of interest apart from, groups F04F5/02 - F04F5/42
    • F04F5/46—Arrangements of nozzles
    • F04F5/465—Arrangements of nozzles with supersonic flow

Definitions

  • the present invention relates to a compressor device with at least one compressor with an inlet and an outlet.
  • the invention concerns a compressor device with at least one compressor with an inlet and an outlet and a channel for channelling the gas flow drawn in by the compressor and the gas flow compressed by the compressor to a consumer downstream from the compressor.
  • Such a compressor device can be used to compress air or another gas or mixture of gases for example, whereby this compressed gas can supply a compressed air installation or another consumer of compressed gas and/or compressed air for example.
  • compressed air is stated hereinafter it must also be taken to mean other compressed gases and/or mixture of gases.
  • the compressor device there is a pressure vessel between the compressor and the consumer(s) that acts as a buffer for compressed air to stabilise the pressure of the compressed air that is supplied to the consumers.
  • a non-return valve is also provided between the compressor and the consumers that prevents compressed air from being able to flow back to the compressor from the pressure vessel when the compressor is not supplying any compressed air to this pressure vessel.
  • Such a non-return valve generally comprises a valve disk that is pushed against a seat by means of a spring and the pressure in the pressure vessel, and thus makes a reverse flow of compressed air from the pressure vessel to the compressor impossible.
  • a reverse speed higher than the maximum allowed reverse speed could lead to failure of the compressor, which could have adverse effects on the safety of the compressor device as it could lead to breakages which, in the worst case, could give rise to the breaking off of a part that is thrown out at high speed, which constitutes a risk for any bystanders.
  • the scroll compressor having a suction chamber communicating with the compression chambers, a discharge chamber, an oil separation chamber separating lubricating oil from the refrigerant gas and communicating with the discharge chamber and a back pressure chamber provided in front of the movable scroll member.
  • a possible additional measure can consist of providing a release valve that can open when the compressor is not operating to allow a proportion of the compressed air to escape from the installation via this valve, such that the reverse turning of the compressor can be limited.
  • Another possible additional measure provides an inlet throttle or inlet vanes that automatically close when the compressor is not operating, such that too high a reverse speed of the compressor can be prevented.
  • a disadvantage of such a release valve and such an inlet throttle or inlet vanes is that they must be actively controlled, i.e. they must be opened or closed at the appropriate time, which makes such facilities liable to failure such that these facilities consequently must satisfy strict safety standards, which affects the cost.
  • directly driven compressors in other words compressors that are driven directly by the motor without the intervention of a gearbox, the braking effect of such a gearbox is absent, which increases the risk of breakage in the compressor.
  • the purpose of the present invention is to provide a solution to one or more of the aforementioned and/or other disadvantages.
  • the object of the present invention is a compressor device with at least one compressor with an inlet and an outlet and a channel for channelling the gas flow drawn in by the compressor and the gas flow compressed by the compressor to a consumer, whereby this compressor device is provided with a passive element that limits the backflow of the compressed gas from the consumer to the aforementioned inlet to a set maximum flow.
  • the passive element comprises a sonic nozzle.
  • An advantage is that such a passive element will be able to limit the speed of the compressor during reverse turning and will thereby be able to prevent damage or limit the risk thereof.
  • 'Passive element' means an element that contains no moving parts which means that such an element has a much lower risk of failure than elements with moving and/or actively controlled components, such that less stringent safety requirements are imposed and the element and the entire device can be constructed more easily and cheaply.
  • the device is provided with a non-return valve, which during normal operation prevents the backflow of the compressed gas to the inlet.
  • the aforementioned passive element will ensure that the reverse turning of the compressor is limited in the event of failure of the non-return valve.
  • the passive element comprises a restriction in the channel for the backflow of the compressed gas from the pressure vessel to the aforementioned inlet.
  • Such a restriction has the advantage that it can be easily constructed and applied in different locations, such as for example at the level of the inlet and/or the outlet of the compressor.
  • the aforementioned restriction in the channel forms the minimum cross-section of the channel that is smaller than the cross-section of the inlet and/or the outlet of the compressor.
  • the set maximum flow is imposed by the maximum allowed speed for the reverse turning of the compressor.
  • the maximum allowed speed for reverse turning is determined by the mechanical limits of the compressor, for example.
  • the set maximum flow rate can be chosen such that the speed of the reverse turning of the compressor is limited to a speed that is less than the maximum allowed speed for reverse turning, such that during reverse turning any form of damage can be prevented.
  • the compressor device 1 according to the invention shown in figure 1 comprises one compression stage 2 that comprises a compressor 3 with an inlet 4 and an outlet 5.
  • the compressor 3 concerned is constructed in the form of a screw compressor, but the invention is not limited as such and the compressor 3 concerned can also be constructed in the form of another type of compressor such as a tooth compressor, a scroll compressor, a turbocompressor or another type of compressor. It goes without saying that that the invention is not limited to application with one compression stage, but can also be applied in compressor devices with a number of compression stages, as will be described further.
  • the compressor device further comprises a channel 6 comprising an inlet channel 6a that is connected to the inlet 4 for channelling the gas flow drawn in by the compressor 3 and an outlet channel 6b that is connected to the outlet 5 for channelling the gas flow compressed by the compressor 3 to a consumer 7 of compressed air and/or to a pressure network or consumer network to which one or more consumers 7 are connected, such as for example pneumatic machines or appliances. It is possible that there is a pressure vessel between the compressor 3 and the consumer 7, whereby the compressed gas flow is first channelled to the pressure vessel via the outlet channel 6b before the compressed gas is supplied to the consumer 7.
  • the inlet 4 of the compressor 3 is directly connected to the surrounding air via the inlet channel 6a to draw in the air to be compressed.
  • the inlet 4 of the compressor 3 is connected to a source, reservoir or similar for any type of gas or mixture of gases.
  • the inlet channel 6a contains an inlet filter that is not shown in the drawings.
  • the compressor 3 consists of a screw compressor with a double rotor 8 that is affixed rotatably in a housing 9.
  • the double rotor 8 is formed by two helical rotors 10a and 10b with lobes that mesh together, and which together with the housing 9 define a gas chamber 11 at the inlet 4, which upon the rotation of the rotors 10a and 10b moves from the inlet 4 to the outlet 5 and thereby becomes increasingly smaller so that the gas trapped in this gas chamber 11 is compressed.
  • the shaft 12 of one of the two rotors 10b is coupled to drive means in the form of a motor 13 for driving the screw compressor 3.
  • a cooler 14 is placed in the outlet channel 6b, for example in the form of a heat exchanger.
  • a passive element 15 is placed in the aforementioned outlet channel 6b, in this case downstream from the compressor 3.
  • a non-return valve 16 is also provided in the aforementioned outlet channel 6b that is configured such that it enables a flow from the compressor 2 to the pressure vessel and the consumer 7, but not in the reverse direction.
  • such a non-return valve 16 comprises a valve disk 16a that is pushed against a seat 16c by means of a spring 16b when the pressure downstream from the non-return valve 16 is greater than the pressure upstream from the non-return valve 16.
  • the invention is not limited as such, as the non-return valve 16 can also be constructed in other ways, for example whereby no spring is provided and the valve disk 16a is pushed against the seat 16c under the influence of gravity and/or under the influence of the pressure difference across this non-return valve 16, and more specifically because the pressure downstream from the non-return valve 16 is greater than the pressure upstream therefrom. It goes without saying that a construction of a non-return valve with a spring 16c can also make use of the aforementioned principles of gravity and/or pressure difference for the closing thereof.
  • the passive element 15 can be constructed in different ways.
  • Figure 2 shows a practical embodiment whereby the element 15 is constructed as a step-shaped restriction 17 in the opposite flow direction Q' in the direction from the outlet 5 to the inlet 4 and thus a widening in the forward flow direction Q from the inlet 4 to the outlet 5.
  • cross-section A of the outlet channel 6b upstream from the restriction 17 is smaller than the cross-section B of the channel downstream from the restriction 17.
  • cross-section of the channel is reduced at the level of the step-shaped restriction 17 in the direction from the outlet 5 to the inlet 4.
  • the operation of the compressor device 1 is very simple and as follows.
  • the compressor 3 is driven by the motor 13.
  • the passive element 15 will hereby have no or as good as no appreciable effect on the compressed air that flows through in the forward direction.
  • the compressed air Downstream from the compressor 3, the compressed air is cooled by means of the cooler 14 to ensure that the compressed air is cold enough before being supplied to the consumer 7.
  • the non-return valve 16 is pushed open due to the pressure of the compressed air against the force of the spring 16b such that the compressed air can flow to the consumer 7 in the forward flow direction Q.
  • the compressor 3 can be stopped such that the pressure downstream from the non-return valve 16 is greater than the pressure upstream therefrom. This pressure difference, together with the force of the spring 16b ensures that the valve disk 16a is pushed against the seat 16c. The non-return valve 16 is thus closed, which prevents compressed air flowing back from the consumer 7 through the compressor 3 to the inlet 4 in the reverse flow direction Q'.
  • the presence of the passive element 15 prevents the compressed air from flowing back through the compressor 3 in the reverse flow direction Q' at too high a rate.
  • the restriction may be dimensioned such that the saturation flow rate of the passive element 15 during a backflow from the outlet 5 to the inlet 4 is less than the maximum flow rate imposed by the maximum allowed speed for the reverse turning of the compressor 3.
  • the passive element 15 must be dimensioned such that the total backflow resistance is large enough to limit the backflow rate such that the reverse turning speed of the compressor 3 is kept below a limit value.
  • Figure 3 shows a variant of the compressor device 1 of figure 1 , whereby in this case two compression stages 2a and 2b are provided, each consisting of a compressor 3a, respectively 3b, whereby the compressors 3a and 3b are connected together in series by means of a channel section 6c, such that the first compressor 3a forms a low-pressure stage 2a, while the second compressor 3b forms a highpressure stage 2b.
  • compressors 3a and 3b are directly driven turbocompressors.
  • the passive element 15 is between the two compressors 3a and 3b in the channel section 6c, upstream from the second compressor 3b, whereby in this case a cooler 14 is also provided in the aforementioned channel section 6c, whereby in this case this cooler 14 acts as an 'in tercooler'.
  • the passive element 15 it is also possible for the passive element 15 to be in the inlet channel 6a, upstream from the first compressor 3a, or for the passive element 15 to be in the outlet channel 6b, downstream from the second compressor 3b.
  • the passive element 15 is constructed as a sonic nozzle 18 as shown in figure 4 , whereby the nozzle 18 is integrated in the channel section 6c whereby this channel section 6c has a constant cross-section C.
  • the sonic nozzle 18 is formed by a nozzle whose flow cross-section gradually decreases in the forward flow direction towards the consumer 7 to a minimum cross-section D, which for a forward gas flow in the flow direction Q forms the outlet 19 of the nozzle and which opens out into a wider channel section 6c to the consumer 7.
  • the sonic nozzle 18 causes a small pressure loss in the forward flow direction Q, but in the reverse flow direction Q' behaves as a step-shaped restriction 17 in the channel section 6c whereby the cross-section of this channel section 6c decreases suddenly.
  • the design of the sonic nozzle 18 is such that the speed of a gas that flows through in the forward direction will accelerate, whereby the speed of sound can be reached at the level of the outlet 19 of the nozzle 18.
  • the diameter of the minimum cross-section D at the outlet 19 of the sonic nozzle 18 is such that the maximum flow rate that can flow through the sonic nozzle 18 at the speed of sound in the forward direction is at least equal to the maximum flow rate that can flow through the compressors 3a and 3b in the forward direction.
  • the nozzle 18 is designed such that the maximum flow rate that can flow back through it in the reverse flow direction is imposed by the maximum allowed speed for the reverse turning of the compressors 3a and 3b. After all, the sonic nozzle 18 will behave as a step-shaped restriction 17 in the cross-section of the channel section 6c to prevent or limit the reverse turning speed of the compressors 3a and 3b.
  • the passive element 15 is constructed as a step-shaped restriction 17, as shown in figure 2 .
  • a cooler can be provided at the outlet 5b of the second compressor 3b to cool the compressed air before the supply to the consumer 7, whereby this cooler thus acts as an aftercooler of the compressor device 1.
  • FIGS 5 and 6 show two alternative embodiments of a compressor device 1 according to the invention, whereby in this case the compressor device 1 comprises two compressors 3a and 3b that are connected together in parallel. They can be screw compressors, directly driven turbocompressors or another suitable type of compressor, or any combination of different types of compressors.
  • the compressors 3a and 3b are each placed in a parallel branch 6c', respectively 6c" of the channel 6, whereby the compressors 3a and 3b are connected via a common section of the inlet and outlet channel 6a and 6b, both downstream and upstream from the compressors 3a and 3b.
  • the passive element 15 is provided in the common outlet channel 6b located downstream from the compressors 3a and 3b, and can be constructed as a step-shaped restriction 17 as shown in figure 2 , or as a sonic nozzle 18 as shown in figure 4 , or in the form of another type of passive element that is configured such that in a normal flow direction of the compressed air it causes no or practically no flow resistance, but in a reverse flow direction Q' provides such a resistance that the reverse turning speed of the compressors 3a and 3b is limited to a safe value.
  • the passive element 15 is provided in the upstream common inlet channel 6a.
  • compressors 3a and 3b will simultaneously compress the air drawn in instead of in subsequent stages, as shown in figure 3 .
  • the drawn in gas originates from the same common inlet channel 6a.
  • the passive element 15 will prevent both compressors 3a and 3b from reverse turning at too high a speed by limiting the flow rate of the gas flow that flows back via the outlet channel 6b to the parallel branches 6c' and 6c". This has the advantage that both compressors 3a and 3b can be protected by means of one passive element 15.
  • each of the compressors 3a and 3b has a separate inlet channel 6a', respectively 6a", and that each of these inlet channels 6a' and 6a" is provided with a passive element 15a, respectively 15b, that limits the backflow rate through each of the compressors 3a and 3b in the event of a failure of the non-return valve 16.
  • the passive elements 15a and 15b are placed in the outlet channel 6b', respectively 6b", downstream from the compressor 3a and 3b concerned.
  • the first inlet channel 6a' draws in air while the inlet channel 6a" draws in another type of gas from a source, reservoir or similar.
  • each passive element 15a and 15b will now each prevent the corresponding compressor 3a and 3b from turning again at too high a speed. This has the advantage that each passive element 15a and 15b can be adapted to the specific requirements of the corresponding compressor 3a, respectively 3b.
  • compressor device 1 can hereby be provided with one or more coolers 14 or otherwise, between or after one or more of the compressors 3, 3a, 3b.
  • the passive element 15 in all embodiments described above can be placed at different locations in the compressor device 1, and if desired can be in the inlet or outlet of a compressor 3, 3a, 3b or can be integrated in one of the compressor housings 9. This last one has the advantage that the passive element 15 does not have to be built into the channel 6a, 6b, 6c.
  • the passive element 15 is integrated in a component of the compressor device 1, such as in the non-return valve 16 itself or in the cooler 14 or in the inlet filter or similar.
  • non-return valve 16 can be replaced by movable inlet vanes, an adjustable inlet throttle and/or a release valve that is activated in order to divert the back flowing air to the environment before it can flow back through the compressor.
  • the compressor device 1 can also be used to compress another gas or mixture of gases other than air.
  • the restriction as shown in figure 2 does not need to be limited to one single step-shaped restriction 17, but can also comprise a number of successive step-shaped restrictions 17 or a gradual transition of diameter, in combination or otherwise with one or more step-shaped restrictions 17.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Seal Device For Vehicle (AREA)
  • Compressor (AREA)
EP21164419.0A 2013-09-05 2014-09-02 Compressor device Withdrawn EP3859158A1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
BE2013/0580A BE1021301B1 (nl) 2013-09-05 2013-09-05 Compressorinrichting
PCT/BE2014/000042 WO2015031961A2 (en) 2013-09-05 2014-09-02 Compressor device
EP14776980.6A EP3042080B2 (en) 2013-09-05 2014-09-02 Compressor device
EP17165818.0A EP3214313B1 (en) 2013-09-05 2014-09-02 Compressor device

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP14776980.6A Division EP3042080B2 (en) 2013-09-05 2014-09-02 Compressor device
EP14776980.6A Division-Into EP3042080B2 (en) 2013-09-05 2014-09-02 Compressor device
EP17165818.0A Division EP3214313B1 (en) 2013-09-05 2014-09-02 Compressor device

Publications (1)

Publication Number Publication Date
EP3859158A1 true EP3859158A1 (en) 2021-08-04

Family

ID=49385059

Family Applications (3)

Application Number Title Priority Date Filing Date
EP21164419.0A Withdrawn EP3859158A1 (en) 2013-09-05 2014-09-02 Compressor device
EP17165818.0A Active EP3214313B1 (en) 2013-09-05 2014-09-02 Compressor device
EP14776980.6A Active EP3042080B2 (en) 2013-09-05 2014-09-02 Compressor device

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP17165818.0A Active EP3214313B1 (en) 2013-09-05 2014-09-02 Compressor device
EP14776980.6A Active EP3042080B2 (en) 2013-09-05 2014-09-02 Compressor device

Country Status (5)

Country Link
EP (3) EP3859158A1 (es)
BE (1) BE1021301B1 (es)
ES (2) ES2741199T5 (es)
TR (1) TR201911182T4 (es)
WO (1) WO2015031961A2 (es)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110139989B (zh) 2017-01-31 2021-02-09 株式会社日立产机系统 旋转式容积型压缩机
US11092363B2 (en) * 2017-04-04 2021-08-17 Danfoss A/S Low back pressure flow limiter

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EP2131040A2 (en) 2008-06-05 2009-12-09 Kabushiki Kaisha Toyoda Jidoshokki Motor-driven scroll type compressor
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Publication number Priority date Publication date Assignee Title
DE518453C (de) 1927-11-18 1931-02-16 Sven Lindequist Schnellaufender Verdichter, insbesondere zum Vorverdichten von Luft oder eines Brennstoffluftgemisches zur Speisung von Hoehenmotoren
US3184155A (en) * 1963-04-17 1965-05-18 Cooper Bessemer Corp Motor compressor unit
GB1407887A (en) * 1973-05-14 1975-10-01 Barodyne Inc Flow control apparatus for a centrifugal compressor
DE2945857A1 (de) * 1979-11-14 1981-05-21 Karl Dipl.-Ing. 7000 Stuttgart Schlecht Schraubenverdichter
JPS59218380A (ja) * 1983-05-27 1984-12-08 Hitachi Ltd スクロ−ル圧縮機
US5530214A (en) * 1994-09-20 1996-06-25 The United States Of America As Represented By The Secretary Of The Navy Venturi muffler
DE60123321T2 (de) * 2000-05-17 2007-04-05 Atlas Copco Airpower N.V. Verdichteranlage mit einem gesteuerten Kühlventilator
US6478560B1 (en) * 2000-07-14 2002-11-12 Ingersoll-Rand Company Parallel module rotary screw compressor and method
WO2002025117A1 (en) * 2000-09-19 2002-03-28 Atlas Copco Airpower, Naamloze Vennootschap High-pressure multi-stage centrifugal compressor
EP1491769A1 (en) * 2003-06-27 2004-12-29 Kabushiki Kaisha Toyota Jidoshokki A device having a pulsation reducing structure, a passage forming body and compressor
EP1571337A1 (en) * 2004-03-05 2005-09-07 Corac Group plc Multi-stage No-oil Gas Compressor
JP2006105064A (ja) * 2004-10-07 2006-04-20 Sanden Corp 圧縮機
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ES2741199T3 (es) 2020-02-10
EP3214313A1 (en) 2017-09-06
EP3042080B1 (en) 2019-05-08
WO2015031961A2 (en) 2015-03-12
ES2874254T3 (es) 2021-11-04
EP3042080B2 (en) 2022-08-10
EP3214313B1 (en) 2021-03-24
EP3042080A2 (en) 2016-07-13
TR201911182T4 (tr) 2019-08-21
WO2015031961A3 (en) 2015-05-07
BE1021301B1 (nl) 2015-10-26
ES2741199T5 (es) 2022-11-24

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