EP2174079B1 - Installation frigorifique - Google Patents

Installation frigorifique Download PDF

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Publication number
EP2174079B1
EP2174079B1 EP08758231A EP08758231A EP2174079B1 EP 2174079 B1 EP2174079 B1 EP 2174079B1 EP 08758231 A EP08758231 A EP 08758231A EP 08758231 A EP08758231 A EP 08758231A EP 2174079 B1 EP2174079 B1 EP 2174079B1
Authority
EP
European Patent Office
Prior art keywords
refrigeration system
valve
valve element
rotor
distributor
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.)
Not-in-force
Application number
EP08758231A
Other languages
German (de)
English (en)
Other versions
EP2174079A1 (fr
Inventor
Hans Kurt Petersen
Allan Juhl Moustgaard
Jorgen Holst
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.)
Danfoss AS
Original Assignee
Danfoss AS
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 Danfoss AS filed Critical Danfoss AS
Publication of EP2174079A1 publication Critical patent/EP2174079A1/fr
Application granted granted Critical
Publication of EP2174079B1 publication Critical patent/EP2174079B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/48—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow path resistance control on the downstream side of the diverging point, e.g. by an orifice
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2511—Evaporator distribution valves

Definitions

  • the invention relates to a cooling system with a refrigerant circuit having a plurality of evaporator sections and a distribution of refrigerant on the evaporator sections causing distribution, which has a controllable valve for each evaporator section.
  • Such a cooling system is off DE 195 47 744 A1 known.
  • the known cooling system has a single compressor and a single condenser, but two separately formed evaporator.
  • the refrigerant flow delivered by the compressor is split into two partial flows after the condenser and before the expansion valves with the aid of a 3/2-way valve, whereby the position of the 3/2-way valve is controlled by a control unit.
  • This training however, only a division of the refrigerant flow to two evaporation sections is possible.
  • JP-A-2003 00 4340 discloses a refrigeration system according to the preamble of claim 1.
  • the invention has for its object to achieve a desired operation of the cooling system with simple means.
  • the distributor has a housing and a rotor rotatably mounted in the housing, the circumference of which has only a radially directed projection which cooperates with a respective valve element of a valve, and the distributor only has a jump, which alternately opens the various valves.
  • cooling system includes, in particular, cooling systems, freezer systems, air conditioning systems and heat pumps.
  • the term "refrigeration plant” has been used for convenience only.
  • the evaporator sections can be arranged in different evaporators. The invention will be explained for the sake of simplicity in the context of multiple evaporators. However, the invention is also applicable when an evaporator has several individually or in groups controllable evaporator sections.
  • the distributor thus has, for each evaporator section, a controllable valve that can be controlled by the radially directed projection of the rotor.
  • This makes it possible to control the individual evaporator sections individually, i. It is possible to supply each evaporator with the amount of refrigerant it needs. There is no need to worry about the evaporators all having the same flow resistance. It is also of minor importance if the evaporators have to deliver different cooling capacity. An evaporator, which requires a larger cooling capacity, gets correspondingly more refrigerant than an evaporator, which has to provide little cooling capacity.
  • valve of the evaporator which needs more refrigerant, remains open for a longer time with one revolution of the rotor than with an evaporator that requires less refrigerant. Since the rotor has a radially directed projection, it is sufficient if the rotor is sufficiently supported in the radial direction. All other bearings can then be relatively easily formed, because the forces acting here are small. A radially directed projection can also be relatively easily finished, for example in the form of a cam. You can supply more than two evaporator sections with little effort.
  • valve elements are radially movable relative to the axis of rotation of the rotor.
  • the effect of the radially directed projection can be converted directly into a movement of the valve element. This simplifies the construction of the distributor. If the valve elements are radially movable, then there is sufficient space for the arrangement of the valve elements available.
  • each valve member has a return spring urging the valve member toward a valve seat.
  • the valve thus remains closed without the action of the cam or radial projection on the rotor. Only when the projection acts on the valve element, it is lifted against the force of the return spring from the valve seat and thus opens the valve.
  • the return spring is supported in a cage insert, which is arranged in an outlet opening of the housing.
  • the cage insert is on the one hand able to support the return spring so that it can exert the necessary closing force on the valve element.
  • the cage insert also has one or more passage openings of sufficient size so that refrigerant flowing through a gap between the valve element and the valve seat can also flow through the cage insert into the corresponding outlet of the distributor.
  • the cage insert has a guide opening for the valve element, in which a shaft of the valve element is guided.
  • the cage insert thus not only supports the return spring, but also guides the valve element linearly, so that the valve element can not tip over the valve seat or only to a permissible degree. This ensures that the valve can close tightly.
  • the cage insert is press-fitted in the outlet opening.
  • the pre-assembled cage insert with return spring and valve element is simply pressed into the outlet opening of the housing.
  • the resulting frictional forces are sufficient to hold the cage insert in the housing.
  • the forces acting on the cage insert forces are already relatively low anyway. They sit together with the valve element open by the force of Return spring and the pressure exerted by the refrigerant on the valve element
  • a plunger is arranged between the rotor and each valve element.
  • the plunger forms a transmission element between the rotor and the valve element. This makes it possible to actuate valves in a relatively small rotor when they are arranged on a larger radius. This creates the opportunity to accommodate a sufficient number of valves. In addition, one has greater constructive freedom.
  • the plunger has a length which is shorter than a distance between a valve element which bears against the valve seat, and the rotor outside the projection.
  • a distance between a valve element which bears against the valve seat, and the rotor outside the projection When the valve is closed so there is a game between the plunger and the rotor. This can ensure that the valve remains closed in any case, when the plunger is not acted upon by the radial projection on the rotor.
  • the clearance can be sized to ensure that the valves close securely over the entire temperature range for which the manifold is approved.
  • the housing has a circumferential projection through which the plungers pass.
  • the projection may also be interrupted in the circumferential direction, as long as it is ensured that there is a bore or passage for each valve, through which the plunger is guided.
  • the plungers are held in a plunger retaining ring.
  • the plunger retaining ring is inserted into the housing. If he together with the circulating Projection is used, then it is ensured that the plunger are supported at two spaced in the direction of movement points. This makes it possible to ensure in the long term that the plunger and the valve elements always keep a predetermined orientation to each other.
  • the plungers preferably have a diameter reduction at their end facing the respective valve element.
  • the plunger can thus be provided over the greater part of its length with a sufficiently large diameter, so that it can absorb the pressure forces which are transmitted from the projection of the rotor to the respective valve element. If he has a taper at its tip, then he is able to pass far enough through the opening, on the outside of the valve seat is formed. Thus, it is possible to open the valves sufficiently far, so that the flow resistance for the refrigerant can be kept small.
  • each valve element is cone-shaped. This makes it easy to achieve a seal between the valve seat and valve element.
  • the valve element can also be guided a little way through the opening, on the outside of the valve seat is formed so that it can be easily reached by the plunger.
  • Fig. 1 shows a schematic representation of a cooling system 1, in which a compressor 2, a condenser 3, a collector 4, a manifold 5 and an evaporator assembly 6 with a plurality of evaporators arranged in parallel 7a - 7d are interconnected in a circuit.
  • the evaporator assembly 6 may also include a single evaporator having a plurality of evaporator sections to be controlled individually or in groups. It is also possible to provide the evaporator assembly 6 with a plurality of evaporators, at least one of which has a plurality of evaporator sections.
  • liquid refrigerant evaporates in the evaporators 7 a - 7 d, is compressed by the compressor 2, liquefied in the condenser 3 and collected in the collector 4.
  • the distributor 5 is intended to distribute the liquid refrigerant to the individual evaporators 7a-7d.
  • a temperature sensor 8a - 8d is arranged at the output of each evaporator 7a - 7d.
  • the temperature sensor 8a-8d detects the temperature of the refrigerant leaving the evaporator 7a-7d. This temperature information is forwarded to a control unit 9, which controls the distributor 5 as a function of the temperature signals of the temperature sensors 8a-8d.
  • the Fig. 2 to 7 now show the manifold 5 in a partially schematic representation.
  • the distributor 5 has a drive motor 10, which is designed, for example, as a stepper motor.
  • the drive motor 10 is mounted on a housing 11 having a in Fig. 2 not visible input and multiple outputs 12 has.
  • the control unit 9 may be integrated. However, it is also possible to arrange the control unit 9 separately from the engine 10 and to supply the engine 10 only with signals from the control unit 9.
  • FIG. 3 shows the distributor 5 from above, with the motor 10 has been removed so that one can see into the interior of the distributor.
  • the motor 10 serves as shown in FIG Fig. 2 can be seen, at the same time as a cover for the housing. Between the motor 10 and the housing 11, a seal 13 is arranged, which prevents refrigerant from the housing 11 can escape.
  • the motor 10 drives a rotor 14, which is arranged in the housing 11.
  • the rotor 14 has a radial projection 15, which has the shape of a cam with two bevelled edges 16, 17.
  • the projection 15 acts on a plunger 18 and deflects it radially outward.
  • the plungers 18 are held in a plunger retaining ring 19.
  • the housing 11 has a projection 20 which projects into a distribution chamber 21.
  • the plungers 18 are held in the projection 20 a second time.
  • the distribution chamber 21 connects the input to the valves 22, one of which is provided for each output 12. In a jump before 15 on the rotor 14 so one of the six valves 22 may be open. The opening time determines the amount of refrigerant that can flow through the corresponding valve and thus the corresponding output 12.
  • the valves 22 are constructed equal to each other.
  • Each valve 22 has a valve element 23 which cooperates with a valve seat 24.
  • the valve element 23 has a cone-shaped head 25 which is guided through a housing wall 26, on the radial outer side of the valve seat 24 is arranged.
  • the valve element 23 is pressed with its head 25 by the force of a return spring 27 in the direction of the valve seat 24.
  • the return spring 27 engages the radially outer side of the head 25.
  • a shaft 28 of the valve member 23 extends radially outward.
  • the shaft 28 has a smaller diameter than the head 25, so that the return spring 27 has a sufficient contact surface.
  • the return spring 27 is supported at its other end to a cage insert 29 which is pressed into an outlet opening 30.
  • the cage insert 29 is thus seated with a press fit in the housing 11.
  • the cage insert 29 has a plurality of legs 31, with which it is held in the housing 11. In between there are intermediate spaces through which the refrigerant can flow into the corresponding outlet 12 when the valve 22 is open, that is, from the valve seat 24, lifted valve element 23.
  • the cage insert 29 has a guide opening 34 and guides the shaft 28 of the valve element 23 so that the valve element 23 is sufficiently secured against tilting. This avoids tilting of the valve element 23 relative to the valve seat 24, provided that it goes beyond a predetermined extent.
  • the plungers 18 are shorter than a distance between the valve element 23 and the rotor 14 in the areas outside of the radial jump ahead 15. This always results in a certain play between the Rotor 14 and the plunger 18, which cooperates with a closed valve or between the plunger 18 and the valve element 23. Thus, one can ensure in a simple manner that when the projection 15 on the rotor 14, the corresponding valve 22 is not aware should open, the valve is closed.
  • the plunger 18 has a diameter reduction 32 at its end, which cooperates with the valve element 23. This makes it possible, on the one hand, to ensure that the plunger 18 has a sufficient cross section in order to be able to absorb the pressure forces exerted by the projection 15 without deformation. On the other hand, in the region in which it cooperates with the valve element 23, it is thin enough to fit through the opening 33 in the wall 26 of the housing, on the radial outer side of which the valve seat 24 is arranged. It is therefore possible to ensure that, even when the plunger 18 with its diameter reduction 32 projects into the opening 33, a sufficient flow cross-section for the refrigerant through the corresponding valve 22 is provided.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Sliding Valves (AREA)
  • Magnetically Actuated Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Details Of Measuring And Other Instruments (AREA)

Claims (12)

  1. Installation frigorifique dotée d'un circuit de réfrigérant qui présente plusieurs parcours d'évaporation et un distributeur provoquant une distribution de réfrigérant aux parcours d'évaporation, lequel distributeur présente une soupape pouvant être commandée pour chaque parcours d'évaporation, caractérisée en ce que le distributeur (5) présente un boîtier (11) et un rotor (14) logé de manière rotative dans le boîtier (11), dont la périphérie ne présente qu'une saillie dirigée dans le sens radial (15) qui coagit avec un élément (23) d'une soupape (22), et en ce que le distributeur ne présente que la saillie (15) qui ouvre en alternance les différentes soupapes.
  2. Installation frigorifique selon la revendication 1, caractérisée en ce que les éléments de soupape (23) peuvent être déplacés dans le sens radial par rapport à l'axe de rotation du rotor (14).
  3. Installation frigorifique selon la revendication 2, caractérisée en ce que chaque élément de soupape (23) présente un ressort de rappel (27) qui le presse en direction d'un siège de soupape (24).
  4. Installation frigorifique selon la revendication 3, caractérisée en ce que le ressort de rappel (27) est en appui dans un insert de cage (29) disposé dans une ouverture d'évacuation (30) du boîtier (11).
  5. Installation frigorifique selon la revendication 4, caractérisée en ce que l'insert de cage (29) présente une ouverture de guidage (34) pour l'élément de soupape (23), dans laquelle une tige (28) de l'élément de soupape (23) est guidée.
  6. Installation frigorifique selon la revendication 4 ou 5, caractérisée en ce que l'insert de cage (29) est disposé en ajustement serré dans l'ouverture d'évacuation (30).
  7. Installation frigorifique selon l'une quelconque des revendications 1 à 6, caractérisée en ce qu'un poussoir (18) est disposé entre le rotor (14) et chaque élément de soupape (23).
  8. Installation frigorifique selon la revendication 7, caractérisée en ce que le poussoir (18) présente une longueur qui est plus courte qu'une distance entre un élément de soupape (23) qui repose sur le siège de soupape (24), et le rotor (14) en dehors de la saillie (15).
  9. Installation frigorifique selon la revendication 7 ou 8, caractérisée en ce que le boîtier (11) présente dans une chambre (21) qui relie une entrée de distributeur aux soupapes (22), une saillie périphérique (20) traversée par les poussoirs (18).
  10. Installation frigorifique selon l'une quelconque des revendications 7 à 9, caractérisée en ce que les poussoirs (18) sont maintenus dans un anneau de retenue de poussoir (19).
  11. Installation frigorifique selon l'une quelconque des revendications 7 à 10, caractérisée en ce que les poussoirs (18) présentent une diminution de diamètre (32) sur leur extrémité tournée vers l'élément de soupape respectif (23).
  12. Installation frigorifique selon l'une quelconque des revendications 1 à 11, caractérisée en ce que chaque élément de soupape (23) est réalisé en forme de cône.
EP08758231A 2007-06-19 2008-06-17 Installation frigorifique Not-in-force EP2174079B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007028562A DE102007028562B4 (de) 2007-06-19 2007-06-19 Kühlanlage
PCT/DK2008/000222 WO2008154922A1 (fr) 2007-06-19 2008-06-17 Installation frigorifique

Publications (2)

Publication Number Publication Date
EP2174079A1 EP2174079A1 (fr) 2010-04-14
EP2174079B1 true EP2174079B1 (fr) 2011-04-13

Family

ID=39735272

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08758231A Not-in-force EP2174079B1 (fr) 2007-06-19 2008-06-17 Installation frigorifique

Country Status (9)

Country Link
US (1) US8794028B2 (fr)
EP (1) EP2174079B1 (fr)
JP (1) JP5185376B2 (fr)
CN (1) CN101784849B (fr)
AT (1) ATE505697T1 (fr)
DE (2) DE102007028562B4 (fr)
MX (1) MX2009013754A (fr)
RU (1) RU2415353C1 (fr)
WO (1) WO2008154922A1 (fr)

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DE102007028565A1 (de) * 2007-06-19 2008-12-24 Danfoss A/S Kühlanlage
KR101479683B1 (ko) * 2013-10-29 2015-01-08 한국지역난방공사 간접 증발냉각기용 미세유량 급수조절식 주수장치
US9915456B2 (en) 2015-06-03 2018-03-13 Mitsubishi Electric Research Laboratories, Inc. System and method for controlling vapor compression systems
CN107923681B (zh) * 2015-09-09 2020-05-05 三菱电机株式会社 空调装置
DE102019201015A1 (de) 2018-02-07 2019-08-08 Robert Bosch Gmbh Mehrwegeventil, insbesondere für ein Fahrzeug-Heiz/Kühl-System
US10982707B2 (en) * 2018-08-21 2021-04-20 Goodrich Corporation Tie bolt retention
CN108954897B (zh) * 2018-09-19 2024-05-21 珠海格力电器股份有限公司 多联机组、末端分配系统及其控制方法与分配器

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Also Published As

Publication number Publication date
CN101784849A (zh) 2010-07-21
MX2009013754A (es) 2010-01-26
ATE505697T1 (de) 2011-04-15
DE102007028562B4 (de) 2009-03-19
DE502008003184D1 (de) 2011-05-26
JP2010530519A (ja) 2010-09-09
US8794028B2 (en) 2014-08-05
DE102007028562A1 (de) 2009-01-02
JP5185376B2 (ja) 2013-04-17
WO2008154922A1 (fr) 2008-12-24
US20100307190A1 (en) 2010-12-09
EP2174079A1 (fr) 2010-04-14
RU2415353C1 (ru) 2011-03-27
CN101784849B (zh) 2012-01-11

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