WO2020259901A1 - Procédé de création d'une variance de capacité maximale d'un détendeur - Google Patents

Procédé de création d'une variance de capacité maximale d'un détendeur Download PDF

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Publication number
WO2020259901A1
WO2020259901A1 PCT/EP2020/062227 EP2020062227W WO2020259901A1 WO 2020259901 A1 WO2020259901 A1 WO 2020259901A1 EP 2020062227 W EP2020062227 W EP 2020062227W WO 2020259901 A1 WO2020259901 A1 WO 2020259901A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
capacity
controlling part
flow
expansion valve
Prior art date
Application number
PCT/EP2020/062227
Other languages
English (en)
Inventor
Kurt Harck
Original Assignee
Danfoss A/S
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 A/S filed Critical Danfoss A/S
Publication of WO2020259901A1 publication Critical patent/WO2020259901A1/fr

Links

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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present invention relates to a method for creating a maximum capacity vari ance of an expansion valve, the expansion valve comprising a valve housing hav ing a valve seat at an end of a valve seat channel and a valve element.
  • An expansion valve is used, for example, in a refrigeration system upstream an evaporator to control a pressure within the evaporator.
  • the expansion valve In order not to waste en ergy and to have a good control behaviour of the circuit, the expansion valve must be adapted to the other components of such a circuit.
  • the object underlying the invention is to have a simple and cost-effective way to provide expansion valves having different maximum flow capacities.
  • This object is solved with a method as described at the outset in that the variance is created by using a valve element having a capacity controlling part and a flow controlling part, wherein different capacity controlling parts are used to adjust the maximum capacity variance.
  • valve housing for different maximum capacities of the expansion valve.
  • the different maximum capacities are deter mined by the different capacity controlling parts of the valve elements.
  • the flow controlling is not ad versely influenced by the capacity controlling part. The flow can still be controlled by the valve element, more precisely by the flow controlling part of the valve ele ment.
  • the maximum capacity variance is solely created by using the different capacity controlling parts. In this case, it is especially easy to obtain a desired specific maximum capacity variance, respectively.
  • the capacity variance is adjusted (or created solely) by using capacity controlling parts with different shapes.
  • the capacity con trolling part extends at least partly into the valve seat channel, so that a circum ferential gap remains between the capacity controlling part and a circumferential wall of the valve seat channel.
  • An area of this gap basically determines the max imum flow capacity of the expansion valve.
  • the gap forms a flow resistance. This flow resistance can be changed by varying a distance between the capacity con trolling part and the wall of the valve seat channel. Since the maximum pressure, which is supplied to the expansion valve, is known, the flow resistance created by the gap determines the maximum flow capacity of the expansion valve.
  • the capacity variance is created by using different capacity con trolling parts, wherein the different capacity controlling parts have different cross- sectional areas with respect to a longitudinal axis of the respective capacity con trolling part.
  • the valve seat channel may be (at least substantially) rotationally symmetric to a longitudinal axis of the valve seat channel.
  • the capacity controlling parts may be (at least substantially) rotationally symmetric about a longitudinal axis thereof, re spectively.
  • the longitudinal axis of the valve seat channel and the longitudinal axis of the respective capacity controlling part, which is used, may coincide.
  • the capacity variance is adjusted (or created solely) by using capacity controlling parts with different diameters.
  • the gap re maining between the capacity controlling part and the circumferential wall of the valve seat channel, which is a ring wall in this case, is ring-shaped.
  • the ring- shaped gap forms the flow resistance.
  • the flow resistance can be changed by varying a radial distance between the capacity controlling part and the wall of the valve seat channel.
  • valve elements are used having a capacity controlling part of cylindrical form.
  • the valve seat channel may be of cylindrical form as well. The result is that the ring-shaped gap has an annular cross section. This simplifies the calculation of the maximum capacity of the expansion valve and the production of the expansion valve.
  • valve elements are used having a capacity controlling part which ends within the valve seat channel remote from the valve seat in a fully open state of the expansion valve.
  • the capacity controlling part projects into the valve seat channel when the expansion valve is fully open.
  • the capacity controlling part may extend over a considerable length of the valve seat channel when the valve seat is in the fully open state.
  • the capacity controlling part ex tends over a length within the valve seat channel, which corresponds at least to a half of a diameter of the valve seat channel (even more preferred at least three- quarters of the diameter of the valve seat channel), when the expansion valve is in the fully open state.
  • the capacity controlling part can be so long that the capacity controlling part extends out of the valve seat channel in a closed state of the expansion valve, respectively.
  • the capacity con trolling part extends over a considerable length of the valve seat channel.
  • the capacity controlling part can be so long that it extends out of the valve seat channel even in the fully open state of the expansion valve.
  • valve elements are used with a length of the capacity controlling part being larger than half a maximum stroke strength of the valve element, more pref erably larger than three-quarters of the maximum stroke length, and most prefer ably at least the stroke length. This helps to ensure that the capacity controlling part is long enough to project into the valve seat channel even if the expansion valve is in the fully open state.
  • valve elements are used with the length of the capac ity controlling part and a length of the flow controlling part are together larger than the maximum stroke length of the valve element.
  • a valve element having the flow con trolling part between the capacity controlling part and a valve element body.
  • the valve element body is a part of the valve element which is used, for example, for guiding the valve element in the valve housing.
  • the flow controlling part has an at least sub stantially tapered shape. This allows regulating the flow through the expansion valve more precisely depending on an opening degree of the expansion valve.
  • a flow cross-sectional area between the flow controlling part and the valve seat may increase if the opening degree of the expansion valve is increased.
  • the opening degree may be increased by retracting the flow con trolling part further out of the valve seat channel.
  • the flow controlling part is of conical form. This simplifies the production.
  • shapes of the flow controlling parts may be adapted to the respective shapes of the capacity controlling parts.
  • a connection part of the valve element where the capacity controlling part is connected with the flow controlling part does not exhibit a step. This improves the flow characteristics and hence the efficiency of the ex pansion valve.
  • the diameter of the flow controlling part at its distal end, which is connected to the capacity controlling part may be the same as the diameter of the capacity controlling part.
  • valve elements are used having different flow controlling parts.
  • the shapes of the flow controlling parts may be adapted to the different capacity controlling parts.
  • they may be adapted such there is no step at a connecting portion where the capacity controlling part is connected to the flow controlling part of the respective valve.
  • a degree of how much the flow controlling part is tapered in total may be adapted to the shape, in particular to the diameter of the respective capacity controlling part of the same valve ele ment.
  • the flow controlling parts may differ in the shape how they are tapered.
  • conical-shaped tapered, convex shaped tapered and/or concave-shaped tapered flow controlling parts may be used.
  • Fig. 1 shows a cross-sectional view of an expansion valve having a valve el ement with a capacity controlling part according to a first embodiment, wherein the expansion valve is in a closed state.
  • Fig. 2 shows a cross-sectional view of a main part of an expansion valve hav ing the same valve housing as the expansion valve shown in Fig. 1 and a valve element with a different capacity controlling part according to a second embodiment, wherein the expansion valve is in a closed state.
  • Fig. 3 shows a cross-sectional view of a central part of the expansion valve of Fig. 2, wherein the expansion valve is in an almost fully open state.
  • Fig. 4 shows a cross-sectional view of a central part of an expansion valve having the same valve housing as the expansion valves shown in Fig. 1 and Fig. 2 and a different valve element with a capacity controlling part according to a third embodiment, wherein the expansion valve is in an almost fully open state.
  • Fig. 5 shows a cross-sectional view of a central part of a further expansion valve having the same valve housing as the expansion valves shown in Fig. 1 , Fig. 2 and Fig. 4 and a valve element with a different capacity controlling part according to a fourth embodiment, wherein the expan sion valve is in an almost fully opened state.
  • An expansion valve 1 shown in Fig. 1 comprises a valve housing 2 and a valve element 3.
  • a valve seat 4 is provided in the valve housing 2.
  • a valve seat chan nel 5 extends from the valve seat 4.
  • the valve seat channel 5 has a cylindrical shape and extends along a longitudinal axis thereof.
  • the valve element 3 comprises a flow controlling part 6 and a capacity controlling part 7.
  • the flow controlling part 6 is in form of a cone. In a closed state of the expansion valve 1 shown in Fig. 1 , the flow controlling part 6 rests against the valve seat 4 and interrupts a fluid connection between two ports 8, 9 of the expansion valve 1.
  • a maximum capacity of the expansion valve 1 is determined by the ca pacity controlling part 7.
  • the capacity controlling part 7 is of cylindrical form. As mentioned above, the valve seat channel 5 is of cylindrical form as well.
  • the capacity controlling part 7 extends, at least in a closed state of the expansion valve 1 , at least to the end of the valve seat channel 5 remote from the valve seat 4. It can, however, extend further, i.e. it can protrude out of the valve seat channel 5.
  • the capacity con trolling part 7 of the valve element 3 covers a substantial part of the length of the valve seat channel 5.
  • the capacity controlling part 7 projects into the valve seat channel 5 even when the expansion valve 1 is in a fully open state.
  • a ring-shaped gap of an annular cross section remains between the capacity con trolling part 7 and the circumferential wall (ring wall) of the valve seat channel 5, in particular even if the expansion valve is in a fully open state.
  • This ring-shaped gap forms a throttling resistance.
  • the magnitude of the resistance in the fully open state is determined by the cross section of the ring-shaped gap.
  • the diameter of the capacity controlling part 7 can be zero meaning that the ca pacity controlling part 7 is not present.
  • the expansion valve has the largest maximum capacity that is possible.
  • the diameter of the flow controlling part 7 is only slightly smaller than an inner diameter of the valve seat channel 5.
  • the ex pansion valve has the smallest maximum capacity.
  • a valve element 3c with a flow controlling part 7c according to a fourth embodiment having a large diameter is depicted in Fig. 5.
  • Fig. 2 shows a cross-sectional view of a main part of another expansion valve in a closed state. Nevertheless, this expansion valve has the some structure and functionalities as the expansion valve 1 shown in Fig. 1 and described above. Identical elements are denoted by the same reference signs and are not described again.
  • the valve housing 2 is identical to the one of Fig. 1.
  • the expansions valve of Fig. 2 comprises a different valve element 3a.
  • a flow controlling part 6a differs from the flow controlling part 6 and a capacity controlling part 7a differs from the capacity controlling part 7.
  • the flow controlling part 6a is rotationally symmetric to a longitudinal axis thereof and is of tapered shape as well.
  • a circumferential groove 62 is provided in an outer circumferential surface of the flow controlling part 6a. Furthermore, a ta pered outer surface 61 a of a portion of the flow controlling part 6a on the side of the capacity controlling part 7a has a convex curvature seen along said longitudi- nal axis (i.e. the portion between the circumferential groove 62 and the capacity controlling part 7b). This provides a more precise control of the flow when the opening degree of the expansion valve is small.
  • Fig. 3 shows a central part of the expansion valve of Fig. 2 including a part of the valve element 3a with the flow controlling part 6a and the capacity controlling part 7a, further the valve seat 4, a part of the valve housing 2 and an upper part of the flow channel 5.
  • the expansion valve is in an almost fully open state.
  • the flow resistance of the whole expansion valve is at least substantially created only (and hence determined) by an annular gap 51 a between a circum ferential (ring) wall of valve seat channel 5 and an outer circumferential surface of the cylindrical capacity controlling part 7a.
  • the capacity controlling part 7a ac cording to this second embodiment has a cylindrical shape as well and a similar diameter compared to the capacity controlling part 7 used in the expansion valve 1 , which is depicted in Fig. 1.
  • the maximum flow capacity of the expansion valve of Fig. 2 and Fig. 3 is similar the maximum flow capacity of the expansion valve 1 of Fig. 1.
  • FIG. 4 A central part of a further expansion valve being in an almost fully open state is depicted in Fig. 4.
  • a valve element 3b has a different flow controlling part 6b and a different capacity controlling part 7b according to a third embodiment.
  • the capacity controlling part 7b is of cylindrical shape but its diameter is larger than the diameter of the capacity controlling part 7a in Fig. 2 and Fig 3.
  • an an nular gap 51 b between the ring wall of valve seat channel 5 and an outer circum ferential surface of the cylindrical capacity controlling part 7b in the fully open position is considerably smaller than the annular gap 51 a.
  • a cross- sectional flow area of the annular gap 51 b is considerably smaller than a cross- sectional flow area of the annular gap 51 a, for example the half. Therefore, the maximum capacity of the expansion valve of Fig. 4 in the fully open state is con siderably smaller than the one of the expansion valve of Fig. 2 and Fig. 3.
  • the shape of the flow controlling part 6b is adapted to the smaller diameter of the capacity controlling part 7b.
  • the flow controlling part 6b is less tapered then the flow controlling part 6a.
  • the flow controlling part 6b is less tapered, a more precise control of the flow is obtained.
  • FIG. 5 Still another expansion valve being in an almost fully open state is depicted in Fig. 5.
  • a valve element 3c according to a fourth embodiment has a different flow controlling part 6c and a different capacity controlling part 7c.
  • the capacity controlling part 7c is of cylindrical shape but its diameter is even larger than the diameter of the capacity controlling part 7b according to the second embodiment, which is shown in Fig. 4.
  • an annular gap 51 c between the ring wall of the valve seat channel 5 and an outer circumferential surface of the capacity controlling part 7c in the fully open position is smaller than the annular gap 51 b.
  • a cross- sectional flow area of the annular gap 51 c is smaller than the cross-sectional flow area of the annular gap 51 b, for example the half. Furthermore, it is considerably smaller than the cross-sectional flow area of the annular gap 51 a, for example a quarter of the latter. Therefore, the maximum capacity of the expansion valve of Fig. 5 with the capacity controlling part 7c according to the fourth is smaller than the one of the expansion valve of Fig. 4 and considerably smaller than the one of the expansion valves of Fig. 2 and Fig. 3.
  • the shape of the flow controlling part 6c is adapted to the shape of the flow con trolling part 7c in the same way as described with regard to the flow controlling part 6b.
  • the maximum capacity of the expansion valves is ad- justed in an easy, cost-efficient and reliable manner by using different valve ele ments 3, 3a, 3b, and 3c having different capacity controlling parts 7, 7a, 7b, and 7c.
  • the different maximum capacities are created by the differ ent diameters of the capacity controlling parts 7, 7a, 7b, and 7c.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Lift Valve (AREA)

Abstract

L'invention concerne un procédé de création d'une variance de capacité maximale d'un détendeur (1) comportant un carter de soupape (2) présentant un siège de soupape (4) à une extrémité d'un canal de siège de soupape (5) et un élément de soupape (3, 3a, 3b, 3c). Il est possible de présenter une manière simple et économique de fournir des détendeurs ayant des capacités d'écoulement maximales différentes. À cet effet, la variance est créée à l'aide d'un élément de soupape (3, 3a, 3b, 3c) ayant une partie de régulation de capacité (7, 7a, 7b, 7c) et une partie de régulation de débit (6, 6a, 6b, 6c), les parties de régulation de capacité différentes (7, 7a,7b, 7c) étant utilisées pour créer la variance de capacité maximale.
PCT/EP2020/062227 2019-06-27 2020-05-03 Procédé de création d'une variance de capacité maximale d'un détendeur WO2020259901A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP19183060.3 2019-06-27
EP19183060 2019-06-27

Publications (1)

Publication Number Publication Date
WO2020259901A1 true WO2020259901A1 (fr) 2020-12-30

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3013767A (en) * 1957-05-27 1961-12-19 Dow Chemical Co Valve
WO2001027543A1 (fr) * 1999-10-08 2001-04-19 Zexel Valeo Climate Control Corporation Cycle frigorifique
DE102005050086A1 (de) * 2004-11-08 2006-05-11 Otto Egelhof Gmbh & Co. Kg Expansionsventil, insbesondere für eine Kältemittelanlage

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3013767A (en) * 1957-05-27 1961-12-19 Dow Chemical Co Valve
WO2001027543A1 (fr) * 1999-10-08 2001-04-19 Zexel Valeo Climate Control Corporation Cycle frigorifique
DE102005050086A1 (de) * 2004-11-08 2006-05-11 Otto Egelhof Gmbh & Co. Kg Expansionsventil, insbesondere für eine Kältemittelanlage

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