EP4288663A1 - Compresseur à piston, plus particulièrement pour pompe à chaleur - Google Patents

Compresseur à piston, plus particulièrement pour pompe à chaleur

Info

Publication number
EP4288663A1
EP4288663A1 EP22702461.9A EP22702461A EP4288663A1 EP 4288663 A1 EP4288663 A1 EP 4288663A1 EP 22702461 A EP22702461 A EP 22702461A EP 4288663 A1 EP4288663 A1 EP 4288663A1
Authority
EP
European Patent Office
Prior art keywords
piston
working
valve
chamber
cylinder
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.)
Pending
Application number
EP22702461.9A
Other languages
German (de)
English (en)
Inventor
Tim HAMACHER
Andreas Mück
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.)
Sph Sustainable Process Heat GmbH
Original Assignee
Sph Sustainable Process Heat GmbH
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=80226015&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP4288663(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Sph Sustainable Process Heat GmbH filed Critical Sph Sustainable Process Heat GmbH
Publication of EP4288663A1 publication Critical patent/EP4288663A1/fr
Pending legal-status Critical Current

Links

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
    • 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
    • F04B39/125—Cylinder heads
    • 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
    • F04B39/10—Adaptations or arrangements of distribution members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type

Definitions

  • Piston compressor in particular for a heat pump
  • the present invention relates to a piston compressor, in particular for a heat pump, with a cylinder, a piston mounted in the cylinder so that it can move linearly along a cylinder longitudinal axis, a working chamber formed in the cylinder and whose volume can be changed by a piston movement and which has a first valve section of a valve device with a Working medium inlet chamber and via a second valve section of the valve device with a working medium outlet chamber is flow-connected, wherein the working space is delimited by an inner jacket of the cylinder, a piston end face formed at a piston end of the piston and a working space head section opposite the piston end face, wherein the working space Head section is formed from a geometric arrangement of the first and second valve sections.
  • the piston compressor proposed according to the invention can be used, for example, in thermodynamic heating systems such as heat pumps, in particular in high-temperature heat pumps.
  • thermodynamic heating systems such as heat pumps
  • high-temperature heat pumps in particular in high-temperature heat pumps
  • an implementation of the present invention in a thermodynamic cooling system for example a refrigerating machine or air conditioning system, is also not ruled out.
  • the piston compressor proposed according to the invention can also be used in other systems.
  • Heat pump technology is well known. Heat pumps are used to absorb thermal energy from a first external medium (e.g. the ambient air or liquids) using technical or mechanical work and to transfer it to a second external medium in addition to the drive energy used as useful energy or useful heat.
  • the second external medium is a medium to be heated.
  • the first external medium can be provided by liquids contained in the earth rock, but waste heat can also serve as the first external medium in industrial processes.
  • Heat pumps are currently used in particular for heating buildings. However, in the meantime applications have also become known in which heat pumps are used to generate the heat required for industrial processes. For industrial processes, high-temperature heat pumps with medium temperatures of > 100°C are often used or required.
  • the heat pump there has a fluid circuit for absorbing thermal energy through the fluid (working medium) from at least one first reservoir using technical work and for delivering thermal energy through the fluid to at least one second reservoir for heating the at least one second reservoir.
  • heat pumps In addition to an evaporation unit, a condensation unit and an expansion unit, heat pumps (including high-temperature heat pumps) have a compressor for compressing a working medium circulating in a fluid circuit as standard.
  • the working medium that has been transported from the liquid to the gaseous state is sucked in by the compressor and compressed to a pressure level that is required to liquefy the working medium.
  • the (e.g. electrically) driven compressor compresses the vaporous working medium from a low initial pressure level to a higher final pressure level, the temperature of the working medium increases.
  • compressor compressor
  • Scroll compressors screw compressors
  • rotary piston compressors rotary piston compressors
  • rotary piston compressors this list is not exhaustive.
  • Reciprocating compressors for example, are based on the principle that a moving piston draws in the gaseous working medium through a suction valve from a suction chamber (working medium - inlet chamber) in the direction of a working space when the piston moves downwards in a cylinder surrounding the piston along a cylinder longitudinal axis. The working medium is compressed when the piston experiences an upward movement along the longitudinal axis of the cylinder.
  • the suction valve is during compression of the work equipment closed.
  • the working medium leaves the working chamber via an outlet valve (pressure valve) in the direction of a working medium outlet chamber if the pressure in the cylinder or in the working chamber exceeds a pressure level present on a high-pressure side of the compressor.
  • the "compressor” can be synonymously referred to as "compressor”.
  • the compressor is commonly referred to as a piston compressor.
  • the actual compressor can interact directly with other components, such as a drive unit driving the compressor (eg an electric motor), a lubricant reservoir.
  • the invention can relate to different designs of compressor systems, including an open compressor system, a semi-hermetic compressor system or a hermetic compressor system.
  • the drive unit (the motor) is structurally separate from the compressor.
  • a drive shaft of the compressor is guided out of the housing and is operatively connected to the drive unit.
  • the drive unit and the compressor are arranged in a common housing.
  • the drive unit and compressor are also arranged in a common housing, but in contrast to a semi-hermetic compressor system, this is completely welded to the outside.
  • the compressors or compressor systems mentioned have a lubricant reservoir for holding a lubricant.
  • a lubricant can also be understood to mean a lubricant mixture.
  • the lubricant serves to lubricate components of the compressor or compressor system, in particular the moving components of the compressor (e.g. pistons, cylinders, bearings, valves, etc.).
  • Known lubricant reservoirs are often referred to as "oil sump". The oil or lubricant is sucked in from the oil sump or lubricant reservoir and transported to the points to be lubricated.
  • Known piston compressors have a working space with a flat working space head section, ie the valve plates used there (these separate the working space from a working medium inlet chamber and a working medium outlet chamber) are flat and vertical to the cylinder longitudinal axis of a cylinder supporting the piston movably along the cylinder longitudinal axis.
  • the end face of the piston opposite the valve plates is also flat.
  • Part of the valve plate area is used for suction valves, the other part for exhaust valves.
  • Such an arrangement causes the suction gas to flow directly past the discharged gas, which can cause undesirable energy or heat losses.
  • the object of the present invention is to provide a piston compressor and a heat pump with improved effectiveness or improved efficiency.
  • the present invention relates to a piston compressor, in particular for a heat pump, with a cylinder, a piston which is mounted in the cylinder to be linearly movable along a cylinder longitudinal axis, a working chamber which is formed in the cylinder and whose volume can be changed by a piston movement and which is connected via a first valve section of a valve device to a working medium inlet chamber and via a second valve section of the valve device to a working fluid outlet chamber, with the working chamber being delimited by an inner jacket of the cylinder, a piston end face formed at a piston end of the piston and a working chamber head section opposite the piston end face, the working chamber head section being formed is made up of a geometric arrangement of the first and second valve sections.
  • the piston compressor according to the invention is characterized in that the first and second valve sections are arranged in such a way that the working chamber tapers in the direction of the working chamber head section.
  • a piston compressor according to the invention can comprise one or more piston-cylinder units.
  • the invention will be explained by way of example using a piston-cylinder unit composed of a piston and a cylinder. Accordingly, each of the piston-cylinder units can have the following features:
  • a working chamber formed in the cylinder and variable in volume by a piston movement, which is flow-connected via a first valve section of a valve device to a working medium inlet chamber and via a second valve section of the valve device to a working medium outlet chamber, the working chamber being delimited is formed by an inner casing of the cylinder, a piston end face formed at a piston end of the piston and a working chamber head section opposite the piston end face, the working chamber head section being formed from a geometric arrangement of the first and second valve sections.
  • the first and second valve sections are arranged in such a way that the working space tapers in the direction of the working space head section.
  • the volume of the working chamber is reduced or increased. It is desirable that the working space has the smallest possible dead volume when the piston is in a position close to the working space head section (ie close to the working medium inlet chamber and working medium outlet chamber).
  • a "linear movement" of the piston is to be understood, in particular, as the piston moving back and forth in an interior space of the cylinder.
  • the working fluid inlet chamber provides a low pressure side of the system while the working fluid outlet chamber provides a high pressure side.
  • a flow connection between the working medium inlet chamber and the working space means that working medium can flow out of the working medium inlet chamber into the working space with a corresponding piston position.
  • the working fluid is then compressed (condensed) in the working space and can flow out of the working space (induced by the piston movement) in the direction of the working fluid outlet chamber.
  • the first and second valve sections can have valve openings (e.g. slits, hole openings) in order to provide the flow connections between the working space and the aforementioned inlet and outlet chambers.
  • the first and second valve section can be designed in a known manner, for example in the form of valve plates.
  • the head section of the working space can be limited solely by the first and second valve sections.
  • the tapering geometry of the working space in the direction of the working space head section ensures that the contact surface between the working space and the respective chambers is enlarged. This increases the for the Valve sections (e.g. valve plates) available area. With the increased area of the valve sections, the pressure loss is reduced.
  • the proposed geometry the working medium flowing into and out of the working space no longer flows directly past one another. Flow separation is improved, avoiding unwanted heat transfer.
  • the first and second valve sections are each arranged at an angle of unequal 90° to the longitudinal axis of the cylinder.
  • the valve device is not arranged perpendicularly to the longitudinal axis of the cylinder, but provides a roof-like cross section, so that the working space tapers in the direction of the working space head section. Since one of the valve sections is flow-connected to the working medium inlet chamber and one of the valve sections to the working medium outlet chamber, such an arrangement prevents the working medium flowing into the working chamber from flowing directly past the working medium flowing out of the working chamber. This also increases the surface area of the valve device—compared to the arrangements known from the prior art.
  • first and second valve sections are arranged at a different angle relative to the longitudinal axis of the cylinder. This means that the first and second valve sections cannot be arranged symmetrically to one another. An asymmetrical arrangement is also possible.
  • the first and second valve sections are at the same angle relative to the longitudinal axis of the cylinder is arranged.
  • the valve sections are arranged symmetrically and preferably have the same shape and dimensions (length, width, diameter), ie they provide the same surface.
  • the working chamber head section terminates at an acute or obtuse angle in relation to its cross section, the acute or obtuse angle being spanned by the first and second valve section.
  • the angle spanned by the first and second valve section can be selected depending on the installation space requirements or structural conditions of the piston compressor.
  • the working chamber head section terminates at a right angle in relation to its cross section, the right angle being spanned by the first and second valve sections.
  • the working chamber head section has a concave cross-sectional shape in the direction of the working chamber.
  • concave can be understood to mean a curved cross section, in which the working space tapers in the direction of the working space head section.
  • concave can also mean an arrangement relating to one of the aforementioned angles between the first and second valve sections.
  • the first and second valve sections are arranged in such a way that they provide a working chamber head section designed in the manner of a hemisphere. This leads to a further increase in the surface area of the valve device or the valve sections when compared to the known systems from the prior art. It should be noted that the increase in surface area compared to the prior art always means a relative increase in surface area based on the respective size of the piston compressor used. According to a further advantageous embodiment of a piston compressor proposed by the invention, it can be provided that the piston end face corresponds geometrically to the working chamber head section. This enables the piston, when compressing the working medium, to displace it as completely as possible from the working space.
  • the piston end face preferably has a convex shape in the direction of the working space head section.
  • the geometric design of the working chamber head section and the piston end face can be designed in the manner of a key-lock principle.
  • the working medium inlet chamber and the working medium outlet chamber are separated from one another by a separator adjoining the working chamber head section.
  • the separator prevents a direct accumulation of material between the working medium contained in the working medium inlet chamber and the working medium outlet chamber (this takes place via the working space), and on the other hand, the separator reduces or reduces heat transfer between the working medium inlet chamber and the working medium outlet chamber prevented.
  • the separator comprises an insulating layer arranged between a wall of the working medium inlet chamber and a wall of the working medium outlet chamber, in particular an air gap. If the insulation layer is an air gap, air provides the thermal insulation medium.
  • the air can be released or added via a suitable valve.
  • Another thermally insulating material can also form the separator or be arranged in a cavity between the working medium inlet chamber and the working medium outlet chamber. Multiple cavity chambers or channels can also be provided to form the separator.
  • the thermally insulating material can also be a ceramic material, a plastic, a composite material, a textile material, glass, an oil or any other suitable insulating medium with thermally insulating properties.
  • the invention also relates to a heat pump, in particular a high-temperature heat pump having a piston compressor(s) designed according to one or more of the invention.
  • a heat pump in which a piston compressor according to the invention is used is preferably a high-temperature heat pump.
  • This can be a high-temperature heat pump with temperatures of the heat-absorbing external medium of >100°C.
  • One or more of the piston compressors described above can be provided, wherein each of the piston compressors can have one or more piston-cylinder units of the type described above. Reciprocating compressors are particularly suitable for this purpose.
  • FIG. 1 shows a section of a piston-cylinder unit of a piston compressor known from the prior art
  • FIG. 2 shows a section of a piston-cylinder unit of a piston compressor designed according to the invention.
  • FIG. 1 shows a section of a piston-cylinder unit of a piston compressor known from the prior art.
  • a cylinder 1 is shown (this can also be referred to as a cylinder housing) and a piston 2 mounted in the cylinder 1 so that it can move linearly along a cylinder longitudinal axis L.
  • a working chamber 3 is formed in the cylinder 1, the volume of which is increased by a piston movement of the piston 2 is changeable.
  • the working chamber 3 is above a first valve section 11 of a valve device
  • the working space 3 is delimited by an inner casing
  • a piston end face 8 formed on a piston end of the piston 2 and a working chamber head section 9 opposite the piston end face 8, the working chamber head section 9 being formed from a geometric arrangement of the first and second valve sections 11, 12
  • the first valve sections 11 are arranged at the same level as the second valve section 12 (this is positioned in the center).
  • the valve sections 11, 12 are arranged at an angle of 90° relative to the longitudinal axis L of the cylinder.
  • the piston 2 has an outside diameter that corresponds to the inside diameter of the cylinder 1 .
  • the piston end face 8 has a geometry that corresponds to the working chamber head section 9 .
  • the piston face 8 is also arranged perpendicularly to the cylinder longitudinal axis L and has a flat shape.
  • the working chamber 3 has—as mentioned—a flat head section 9 of the working chamber. This is flat and perpendicular to the cylinder longitudinal axis L of the piston 2 movably mounted along the cylinder longitudinal axis L cylinder 1 is formed.
  • the valve sections 11, 12 opposite piston end face 8 is also flat.
  • a part of the areas of the first valve portions 11 (there are two first valve portions 11 on the outer sides here) is used for suction valves.
  • Such an arrangement causes the suction gas to flow directly past the discharged gas, which can cause undesirable energy or heat losses.
  • Fig. 2 shows a section of a piston-cylinder unit of a piston compressor designed according to the invention.
  • the first and second valve sections 11 , 12 are arranged in such a way that the working chamber 3 tapers in the direction of the working chamber head section 9 .
  • the head section 9 of the working space is roof-shaped in the present case.
  • the first and second valve sections 11, 12 are each arranged at an angle of unequal 90° to the longitudinal axis L of the cylinder.
  • the piston end face 8 corresponds geometrically to the working chamber - head section 9.
  • the dashed line indicates that the piston end face 8 is also roof-shaped, and in particular has a cross-sectional shape in the manner of a triangle.
  • the tapering geometry of the working space 3 in the direction of the working space head section 9 ensures that the contact surface between the working space 3 and the respective chambers (working medium inlet chamber 5, working medium outlet chamber 6) is enlarged. This increases the area available for the valve sections 11, 12. With the increased area of the valve sections 11, 12, the pressure loss is reduced. In the proposed geometry, the working medium flowing into and out of the working chamber 3 does not flow directly past one another—as in the prior art. Flow separation is improved, avoiding unwanted heat transfer.
  • the working medium inlet chamber 5 and the working medium outlet chamber 6 are separated from one another by a separator 10 (shown dotted) adjoining the head section 9 of the working space.
  • the separator 10 comprises an insulating layer which is arranged between a wall of the working medium inlet chamber 5 and a wall of the working medium outlet chamber 6 and which can be designed in particular in the form of an air gap. This also reduces heat losses.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne un compresseur à piston comprenant : un cylindre (1) ; un piston (2) qui est monté de façon à effectuer un mouvement linéaire le long d'un axe longitudinal du cylindre (L) ; une chambre de travail (3) qui est en communication fluidique avec une chambre d'entrée de milieu de travail (5) au moyen d'une première partie de vanne (11) et à une chambre de sortie de milieu de travail (6) au moyen d'une seconde partie de vanne (12), la chambre de travail (3) étant délimitée par une surface latérale interne (7), une face d'extrémité de piston (8) et une partie tête (9) de chambre de travail, la partie tête (9) de chambre de travail étant formée à partir d'un agencement géométrique des première et seconde parties de vanne (11, 12). Afin d'assurer un meilleur rendement, les première et seconde parties de vanne (11, 12) sont agencées de sorte que la chambre de travail (3) est effilée vers la partie tête (9).
EP22702461.9A 2021-02-04 2022-01-27 Compresseur à piston, plus particulièrement pour pompe à chaleur Pending EP4288663A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021102648.2A DE102021102648B4 (de) 2021-02-04 2021-02-04 Kolbenkompressor, insbesondere für eine Wärmepumpe
PCT/EP2022/051951 WO2022167326A1 (fr) 2021-02-04 2022-01-27 Compresseur à piston, plus particulièrement pour pompe à chaleur

Publications (1)

Publication Number Publication Date
EP4288663A1 true EP4288663A1 (fr) 2023-12-13

Family

ID=80226015

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22702461.9A Pending EP4288663A1 (fr) 2021-02-04 2022-01-27 Compresseur à piston, plus particulièrement pour pompe à chaleur

Country Status (6)

Country Link
US (1) US20240125312A1 (fr)
EP (1) EP4288663A1 (fr)
JP (1) JP2024506988A (fr)
CN (1) CN116829835A (fr)
DE (1) DE102021102648B4 (fr)
WO (1) WO2022167326A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3304341A1 (de) 1983-02-09 1984-08-09 Jan 5106 Rott Wattez Kolbenverdichter mit kombiniertem saug- und druckventil, insbesondere fuer kaeltemaschinen
DE102011086476A1 (de) 2011-09-30 2013-04-04 Siemens Aktiengesellschaft Hochtemperaturwärmepumpe und Verfahren zur Verwendung eines Arbeitsmediums in einer Hochtemperaturwärmepumpe
JP6876463B2 (ja) * 2017-02-24 2021-05-26 株式会社前川製作所 圧縮機用ピストン、圧縮機及びヒートポンプユニット
US10704431B2 (en) * 2017-10-03 2020-07-07 Vianney Rabhi Regenerative valve hydraulic actuator
WO2020064781A1 (fr) * 2018-09-24 2020-04-02 Burckhardt Compression Ag Compresseur à piston à labyrinthe

Also Published As

Publication number Publication date
DE102021102648A1 (de) 2022-08-04
CN116829835A (zh) 2023-09-29
WO2022167326A1 (fr) 2022-08-11
DE102021102648B4 (de) 2022-11-17
US20240125312A1 (en) 2024-04-18
JP2024506988A (ja) 2024-02-15

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