EP2886862B1 - Kompressor - Google Patents

Kompressor Download PDF

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Publication number
EP2886862B1
EP2886862B1 EP13197728.2A EP13197728A EP2886862B1 EP 2886862 B1 EP2886862 B1 EP 2886862B1 EP 13197728 A EP13197728 A EP 13197728A EP 2886862 B1 EP2886862 B1 EP 2886862B1
Authority
EP
European Patent Office
Prior art keywords
compressed air
motor
drive shaft
crankcase
compressor
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.)
Active
Application number
EP13197728.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2886862A1 (de
Inventor
Sebastian Hütter
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.)
Kaeser Kompressoren AG
Original Assignee
Kaeser Kompressoren AG
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
Application filed by Kaeser Kompressoren AG filed Critical Kaeser Kompressoren AG
Priority to ES13197728T priority Critical patent/ES2834456T3/es
Priority to EP13197728.2A priority patent/EP2886862B1/de
Priority to CN201480074375.0A priority patent/CN106164487B/zh
Priority to PCT/EP2014/078112 priority patent/WO2015091587A1/de
Priority to US15/105,819 priority patent/US10677236B2/en
Priority to BR112016013952-6A priority patent/BR112016013952B1/pt
Publication of EP2886862A1 publication Critical patent/EP2886862A1/de
Application granted granted Critical
Publication of EP2886862B1 publication Critical patent/EP2886862B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04B41/02—Pumping installations or systems specially adapted for elastic fluids having reservoirs
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • 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
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/06—Mobile combinations
    • 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
    • F04B39/0005—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 adaptations of pistons
    • 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
    • F04B39/0094—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 crankshaft
    • 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
    • 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
    • F04B39/128—Crankcases
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed

Definitions

  • the present invention is concerned with a compressor, in particular a compressor with a reciprocating compressor.
  • Mobile compressors are used, for example, on construction sites or for manual activities in which compressed air is required for connected compressed air tools.
  • a frequently used type of compressor is the piston compressor, in which air is sucked into one or more cylinders, compressed by a piston and expelled again as compressed air.
  • the amount of air delivered by piston compressors is usually adapted to the respective compressed air requirement by regulating the drive speed of the machine driving the compressor.
  • a compressor with a compressed air sensor is shown, depending on the measured value of which the speed control of a reciprocating compressor runs.
  • piston compressors Due to their cyclical operation, piston compressors do not have a continuous output of compressed air, but generate compressed air in pulses. Therefore, a certain compressed air buffer volume is usually kept in order to dampen the compressed air pulses through the compressor. This buffer volume is conventionally kept in separate storage containers so that compressed air can be made available to a compressed air consumer connected to the storage container at a uniformly high pressure.
  • the pamphlet DE 10 2009 052 510 A1 deals with a speed-controlled piston compressor, which has a light and compact compressed air tank made of plastic.
  • U.S. 6,089,835 A a reciprocating compressor with a compressed air tank, which is formed by a shell housing placed on the outside of the motor housing.
  • the Pamphlet U.S. 5,370,504 A shows a piston compressor in which the compressor cylinders are completely embedded in a storage tank for compressed air.
  • the pamphlet WO 2007/041818 A1 discloses a centrifugal compressor having a compression chamber, a drive motor and a compression rotor on a shaft driven by the drive motor.
  • the radial compressor comprises a housing, in the outer wall of which a compressed air storage tank is arranged.
  • a reciprocating compressor is provided with a motor, a drive shaft connected to the motor and driven by it, a crank drive connected to the drive shaft, at least one compressed air generating device with a piston movable in a cylinder, which is driven by the crank drive , and which is designed to generate compressed air in a compression chamber of the cylinder, a crankcase, which has an inner chamber wall in the form of a hollow body which at least partially accommodates the drive shaft, an outer chamber wall spaced radially from the drive shaft from the inner chamber wall, an end wall, and has a partition wall, and a compressed air storage container which is designed to receive compressed air generated by the compressed air generating device, wherein the compressed air storage container through the inner chamber wall, the outer chamber wall, the end wall and the partition and is formed.
  • a basic idea of the invention consists in embedding the storage container for compressed air generated by the compressor in the crankcase of the compressor by using the space around the drive shaft. This results in a great advantage in that a separate storage container can be dispensed with, which in turn contributes to considerable weight and cost savings.
  • the entire structure of the compressor becomes more compact, so that the compressor remains handy and portable despite the large storage volume.
  • the compressor can furthermore have at least one longitudinal rib which is formed in one piece with the crankcase on the outside of the compressed air storage tank.
  • the compressor can furthermore have a motor support, which accommodates and holds the motor, the crankcase being formed around the motor at a distance from the motor support, and the compressed air storage tank at least partially surrounding the motor between the crankcase and the motor support extends around.
  • the compressed air storage container can enclose the drive shaft in an angular range of 360 °.
  • the ratio of the distance between the axis of rotation of the drive shaft up to the point on the inner wall of the compressed air storage container that is most vertically spaced from the drive shaft to the distance between the axis of rotation of the drive shaft and the top dead center of a piston of the compressed air generating device can be between 0.2 and 1 .
  • the ratio of the distance between the axis of rotation of the drive shaft to the point on the inner wall of the compressed air storage container that is most vertically spaced from the drive shaft to the maximum axial extension of the compressed air storage container 25 can be between 0.3 and 2.5.
  • the compressed air generating device can have at least one compression chamber, and the volume ratio between the volume of the compressed air storage container and the sum of the geometric stroke volumes of the compressor chambers of the compressed air generating device can be between 5 and 25.
  • Fig. 1 shows a schematic representation of a compressor 100 in sectional view.
  • the compressor 100 generally has a motor 40 which can be supported in a motor support 41.
  • the motor 40 can be, for example, an electric motor with speed control. It may be possible to use synchronous motors such as brushless direct current motors or asynchronous motors.
  • the engine 40 drives a drive shaft 24 that extends away from the engine 40 in a crankcase 20.
  • the drive shaft 24 can be arranged essentially concentrically to the cross section of the crankcase shape 20 in the center thereof.
  • the drive shaft 24 is used to drive a crank drive 6, which moves a piston 4 up and down in a cylinder 5, ie the crank drive 6 translates the rotational movement of the drive shaft 24 into a linear movement along the direction of extension of the piston 4 in the cylinder 5 the crank drive 6 have a counterweight, a crank web, a connecting rod, a connecting rod bearing and / or a piston pin.
  • a compression chamber 11 is formed at the head end of the cylinder housing, in which air can be compressed according to the main function of the compressor 100.
  • a fan wheel 45 can then be arranged on the crank drive 6.
  • a core component of the crankcase 20 is the compressed air storage tank 25, the in Fig. 1 is designed as an integral component of the crankcase 20.
  • the crankcase 20 has an inner chamber wall 26a, which can be designed, for example, cylindrical with a circular or polygonal cross section, and which receives the part of the drive shaft 24 close to the engine and supports it in a rotating manner.
  • At least one bearing 28b is therefore arranged in a first bearing seat within the chamber wall 26a.
  • the bearing 28b in the first bearing seat can support a part of the drive shaft 24 remote from the motor between the motor 40 and the crank mechanism 6, ie the bearing 28b supports the crank mechanism 6 overhung.
  • a further bearing 28a can be formed in a second bearing seat within the chamber wall 26a, which can support a part of the drive shaft 24 close to the motor between motor 40 and crank mechanism 6, i.e. the bearing 28a supports the motor 40 on the fly.
  • both bearings 28a and 28b are located in the section of the crankcase 20 which forms the compressed air storage tank 25, the bearing seats of the bearings 28a and 28b can be better aligned with one another. This enables an improved concentricity of the bearing seats to one another. It is possible to machine both bearing seats of the bearings 28a and 28b in the crankcase 20 from one side, especially when the radial extent of the bearing 28a is less than that of the bearing 28b.
  • FIG. 2 To illustrate the geometry of the compressed air storage container 25 is shown in Fig. 2 an exemplary cross section of the compressor 100 along the cross section line AA in FIG Fig. 1 shown.
  • the compressed air storage tank is arranged essentially in a ring around the drive shaft 24.
  • the compressed air storage tank 25 can enclose a minimum angle of 200 °, preferably of at least 240 °, around the drive shaft 24.
  • the crankcase 20 and thus the compressed air storage tank 25 is shown in principle as a hollow cylinder.
  • the compressed air storage container 25 is limited in the radial direction with respect to the axis of rotation of the drive shaft 24 by the inner chamber wall 26a on the one hand and an outer chamber wall 26b on the other hand.
  • the outer chamber wall 26b represents an outer wall of the crankcase 20, which completely accommodates the inner chamber wall 26a in its interior.
  • the topology of the external Chamber wall 26b and the housing formed by the inner chamber wall 26a essentially resembles two cylinders mounted one inside the other, for example circular cylinders, prismatic cylinders or cylinders with a polygonal cross-sectional area.
  • the top surfaces of the cylinder jacket surfaces formed by the outer chamber wall 26b and the inner chamber wall 26a can then be closed by one or more partition walls 34 on the other side or one or more end walls 23 on the other side to form the volume of the compressed air storage tank 25.
  • the partition wall 34 or the partition walls 34 have a main direction of extent which is essentially perpendicular to the axial direction of the drive shaft 24.
  • the end wall 23 has a main direction of extent which is essentially perpendicular to the axial direction of the drive shaft 24 and is spaced from the partition 34 or partition walls 34 by a length which substantially corresponds to the longitudinal extent of the compressed air storage tank 25.
  • the compressed air storage tank 25 can be interrupted in the lateral direction by one or more struts 33.
  • the compressed air storage tank 25 can be stabilized on the one hand, and can be divided into several partial storage volumes on the other hand.
  • These partial storage volumes can be connected to one another via compressed air lines or other connecting lines such as bottlenecks.
  • compressed air coolers and / or valves can advantageously be arranged in the connecting lines.
  • three struts 33 are shown, which divide the completely circumferential compressed air storage tank 25 into three equal partial storage volumes, each of which sweeps 120 ° of the crankcase 20.
  • the struts 33 can for example be formed integrally with the crankcase 20, for example in a common metal casting.
  • FIG. 10 shows a detailed illustration of the compressor 100 from FIG Fig. 1 in longitudinal section.
  • the compressor 100 is in the example Fig. 3 shown as a dry-compressing piston compressor 100 with adjustable speed, which works on the principle of reciprocating piston compression.
  • a dry compressing compressor use an oil-lubricated compressor.
  • the compression can, as in Fig. 3 shown as an example, take place in one stage - but it may also be possible to carry out the compression in several stages.
  • the compressor according to Fig. 3 has a cylinder 5 in a compressor section 1 on the right in the figure, in which a piston 4 for compressing air from the environment is arranged. Air from the environment can be sucked into the compression chamber 11 through an intake opening 3 with an intake valve through an intake air filter 2. This takes place when the piston 4 moves downwards.
  • the linear working movement for the piston 5 is generated via a crank mechanism 6 which is connected to the rotor 43 of the motor 40 via a drive shaft 24.
  • the drive shaft 24 can be mounted rotatably with respect to the crankcase 20 via two bearings 28a and 28b, for example permanently lubricated roller bearings with fixed / loose bearings.
  • the crankcase 20 has a crank drive section 21 which at least partially encloses the crank drive 6, and a storage section 22 which adjoins the crank drive section 21 and is arranged axially between this and the motor 40.
  • the partition 34 separates the compressed air storage tank 25 inside the crankcase 20 from the crank drive section 21, that is, the crank drive 6 itself is not located in the air storage volume of the compressed air storage tank 25.
  • the storage section 22 is thus formed disjoint with the crank drive section 21.
  • the cylinder 5 and the piston 4 are not arranged within the storage section 22, that is to say that the volume of the compressed air storage container does not include the cylinder 5 and the piston 4.
  • the storage section 22 comprises an inner chamber wall 26a, which is hollow or tubular, is arranged around the drive shaft 24 and accommodates the area of the drive shaft 24 leading through the storage section 22 and at least one of the two bearings 28a and 28b.
  • the inner chamber wall 26a can have recesses for one or more bearing seats of the bearings 28a and 28b. In addition, more than two bearings 28a and 28b can be provided.
  • the storage section 22 further comprises an outer chamber wall 26b, which can be arranged concentrically around the inner chamber wall 26a and at a distance therefrom.
  • the inner chamber wall 26a and the outer chamber wall 26b are preferably integral with the crankcase 20, i. designed as an integral part of the crankcase 20.
  • the inner chamber wall 26a and the outer chamber wall 26b define, together with one or more partition walls 34, the plane of extension of which is essentially perpendicular to the axis of rotation of the drive shaft 24, a compressed air storage container 25 of the compressor 100.
  • the compressed air storage container 25 is concentric to the drive shaft 24, at least in sections, annular around the inner chamber wall 26a arranged. In other words, the compressed air storage container 25 thus encloses the drive shaft 24 at least in a partial angular range.
  • the compressed air storage container 25 is arranged completely, that is to say in an angular range of 360 °, around the drive shaft 24.
  • the compressed air storage tank 25 is sealed off by an end wall 23 of the crankcase 20 with respect to the engine area or the engine support 41.
  • the compressed air storage tank 25 thus defines a control volume via the corresponding dimensions of the chamber walls 26a and 26b and the axial distance L3 between the partition walls 34 and the end wall 23 of the crankcase 20, which is used to receive and temporarily store compressed air generated by the piston compressor.
  • the motor support 41 can take over the torque support between the rotor and stator of the motor 40.
  • the motor support 41 can be a component that completely or only partially surrounds the motor 40 and can have closed boundary walls with struts, pillars or the like.
  • the motor support 41 can also function as a completely closed motor housing.
  • the motor support 41 can also form the end wall 23, which in the example of FIG Fig. 3 is arranged between motor 40 and storage section 22. However, it can also be provided to arrange the end wall 23 on the outside of the motor 40, so that the motor 40 at least partially through the Storage section 22 is included, that is to say that the volume of the compressed air storage tank 25 extends in the axial direction of the drive shaft 24 at least partially completely or in a partial angular range around the motor 40.
  • the sucked air is compressed in the compression chamber 11 in a compressor work cycle during the upward movement of the piston 4 and discharged via the outlet opening 7 and an outlet valve arranged therein.
  • the compressed air that is expelled via the outlet opening 7 can be discharged into a compressed air line 8, which can include an area with a cooling line 9 for cooling purposes.
  • a cooling line 9 for cooling purposes.
  • the compressed air passes through the check valve 10 into a compressed air storage container 25 of the compressor 100.
  • Both the crankcase 20 and the engine support 41 can be reinforced by ribs 32. These ribs 32, which can also be attached in a similar form on the outside of the crankcase 20 and / or the motor support 41, contribute to better heat dissipation from the compressed air. It is also possible to optimize the mechanical stability of the compressor 100 in this way.
  • a compressed air delivery line for example a compressed air hose for a compressed air-operated tool, through which the compressed air can be taken from the compressed air storage container 25 as required, can be connected via a compressed air coupling 31.
  • a compressor control 60 can call up the pressure of the compressed air measured by a pressure sensor 27 arranged on the compressed air storage container 25 via a control line 61. Should the measured actual pressure in the compressed air storage tank 25 deviate from the setpoint pressure stored in the compressor control 60, a setpoint speed signal for the motor 40 can be determined from the control deviation, which the compressor control 60 sends as a control signal via a control line 62 to an engine control, for example the frequency converter 70 of an electric motor 40 are output. The frequency converter 70 regulates the speed of the motor 40 as a function of the transmitted control signal.
  • the motor 40 is an electronically commutated synchronous external rotor motor in which the frequency converter 70 is attached directly to the stator 44.
  • the stator 44 carries the stator winding 46 and can be connected to the motor support 41 by means of screws, for example. Via the alternating magnetic field generated in the stator winding 46, the torque required for compressing the compressor 100 is generated in a known manner in interaction with the permanent magnets 48 in the rotor 43 of the motor 40.
  • Fig. 4 shows a longitudinal section through a compact variable-speed piston compressor 100 with an alternative motor design. It differs from the 100 in Fig. 1 essentially that the motor 40 is an internal rotor motor with an external frequency converter.
  • Fig. 5 is a more detailed illustration of the compressor's Fig. 4 shown.
  • the motor 40 has an external frequency converter 70, which is connected to the motor 40 via a motor connection cable 47. If, for assembly reasons, the engine 40 cannot be attached to the crankcase 20 with the engine mount 41, the compressor can use the Fig. 5
  • a cover can be provided as an end wall 23. On the one hand, the cover 23 can fasten the motor 40 to the motor support 41, which can then take on a housing function for the motor 40. On the other hand, the cover 23 can fluidically close the compressed air storage container 25 located in the crankcase 20.
  • the maximum radial extension L2 (distance of the axis of rotation of the drive shaft 24 to the point on the inner wall of the compressed air storage container 25 that is most vertically spaced from the drive shaft 24) in a certain ratio to the compressor length L1 (distance of the axis of rotation of the drive shaft 24 to the top dead center of the piston) stand.
  • the dimension L2 can be less than or equal to the compressor length L1.
  • a ratio of L2 / L1 2/3 is advantageous here.
  • the ratio L2 / L1 can be between 0.2 and 1, preferably between 0.4 and 0.66. Viewed in absolute terms, the dimension L2 can be less than 150 mm in order to ensure, for example, the compactness and thus the hand portability of the compressor 100.
  • the maximum radial extent L2 can be in a certain ratio to the maximum axial extent L3 of the compressed air storage container 25. If the compressed air storage tank 25 is arranged between the crank mechanism 6 and the motor 40, the ratio L2 / L3 can be between 0.3 and 2.5, preferably between 0.5 and 1.33.
  • the volume ratio between the volume V R of the compressed air storage tank 25 and the geometric stroke volume V H of the compressor chamber 11 (or the sum V H of all the stroke volumes V Hi of all the compressor chambers 11 in the case of several cylinders 5) can be set in order to optimally dampen the compressed air pulsations to be able to eliminate.
  • the ratio V R / V H can be between 5 and 25.
  • crankcase 20 together with all chamber walls 26a, 26b and end walls 23 and partition walls 34 can be in the Figs. 1 to 5 be formed completely integrally, for example by a casting process with a lost shape or a rapid prototyping process such as selective laser melting, 3D printing, additive layer manufacturing, electron beam melting, laser deposition welding or similar processes.
  • a casting process with a lost shape or a rapid prototyping process such as selective laser melting, 3D printing, additive layer manufacturing, electron beam melting, laser deposition welding or similar processes.
  • the crankcase 20 and its relevant components such as walls, partition walls and end walls can be produced, for example, in a die-casting process, for example from a light metal such as aluminum or magnesium.
  • FIG. 6 , 7 and 8 show schematic representations of further variants of a compressor 100.
  • the compressors 100 of FIG Fig. 6 and 7th differ from the compressors 100 of the Fig. 1 and 4th essentially in that the second bearing 28a is accommodated in the motor 40 - in Fig. 6 on the side of the engine 40 remote from the crankcase, in Fig. 7 on the side of the engine 40 close to the crankcase.
  • the compressor 100 of Fig. 8 has a crankcase 20 which, together with the motor support 41, forms a compressed air storage tank 25 which is expanded axially on the drive shaft.
  • the compressed air storage tank 25 extends around the engine 40 in the interior of the crankcase 20, which is spaced from the engine support 41 accordingly.
  • the ratio L2 / L1 of the maximum radial expansion L2 to the maximum axial expansion L1 of the Compressed air storage container 25 between 0.12 and 1, preferably between 0.2 and 0.5.
  • the compressed air storage tank 25 can surround the motor 40 in a partial angular range of less than 360 ° or completely, that is to say to a circumference of 360 °. It may furthermore be possible that the compressed air storage tank 25 completely surrounds the motor 40 with respect to the angular range around the drive shaft 24, but only partially surrounds the motor 40 in the axial direction of the motor axis of rotation, that is, is not completely formed as far as the end of the motor support 40 remote from the crankcase .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP13197728.2A 2013-12-17 2013-12-17 Kompressor Active EP2886862B1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
ES13197728T ES2834456T3 (es) 2013-12-17 2013-12-17 Compresor
EP13197728.2A EP2886862B1 (de) 2013-12-17 2013-12-17 Kompressor
CN201480074375.0A CN106164487B (zh) 2013-12-17 2014-12-17 压缩机
PCT/EP2014/078112 WO2015091587A1 (de) 2013-12-17 2014-12-17 Kompressor
US15/105,819 US10677236B2 (en) 2013-12-17 2014-12-17 Compressor
BR112016013952-6A BR112016013952B1 (pt) 2013-12-17 2014-12-17 Compressor de pistão

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13197728.2A EP2886862B1 (de) 2013-12-17 2013-12-17 Kompressor

Publications (2)

Publication Number Publication Date
EP2886862A1 EP2886862A1 (de) 2015-06-24
EP2886862B1 true EP2886862B1 (de) 2020-09-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13197728.2A Active EP2886862B1 (de) 2013-12-17 2013-12-17 Kompressor

Country Status (6)

Country Link
US (1) US10677236B2 (es)
EP (1) EP2886862B1 (es)
CN (1) CN106164487B (es)
BR (1) BR112016013952B1 (es)
ES (1) ES2834456T3 (es)
WO (1) WO2015091587A1 (es)

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DE102017107601B4 (de) 2017-04-10 2019-11-07 Gardner Denver Deutschland Gmbh Verfahren zur Steuerung eines Schraubenverdichters
DE102017107599A1 (de) 2017-04-10 2018-10-11 Gardner Denver Deutschland Gmbh Pulsations-Schalldämpfer für Kompressoren
DE102017107602B3 (de) 2017-04-10 2018-09-20 Gardner Denver Deutschland Gmbh Kompressoranlage mit interner Luft-Wasser-Kühlung
WO2020018067A1 (en) * 2018-07-16 2020-01-23 Dresser-Rand Company Valve unloader assembly
DE102019102387A1 (de) 2019-01-30 2020-07-30 Gardner Denver Deutschland Gmbh Kühlungsanordnung und Verfahren zur Kühlung eines mindestens zweistufigen Drucklufterzeugers
AT17743U1 (de) * 2022-02-07 2023-01-15 Anhui meizhi compressor co ltd Hermetisch gekapselter Kältemittelverdichter

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Publication number Publication date
ES2834456T3 (es) 2021-06-17
BR112016013952A2 (es) 2017-08-08
CN106164487B (zh) 2018-04-03
US10677236B2 (en) 2020-06-09
BR112016013952B1 (pt) 2022-01-25
US20160319809A1 (en) 2016-11-03
EP2886862A1 (de) 2015-06-24
WO2015091587A1 (de) 2015-06-25
CN106164487A (zh) 2016-11-23

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