Patent Grant
10295234
This application claims priority to and the benefit of Chinese Patent Application No. 201610095118.6, entitled “HEAT EXCHANGE DEVICE SUITABLE FOR LOW PRESSURE REFRIGERANT,” filed Feb. 19, 2016, and Chinese Patent Application No. 201620131265.X, entitled “HEAT EXCHANGE DEVICE SUITABLE FOR LOW PRESSURE REFRIGERANT,” filed Feb. 19, 2016, both of which are herein incorporated by reference in their entireties.
The present disclosure relates to heating, ventilating, air conditioning, and refrigeration (HVAC&R) systems, and specifically, to a heat exchange device for a low pressure refrigerant.
Falling-film evaporators have been applied to HVAC&R systems to enhance heat transfer efficiency and reduce refrigerant charge. Unfortunately, typical falling-film evaporators may include a refrigerant dispenser that causes refrigerant to incur a relatively high pressure differential due to typical falling-film evaporators used in systems that utilize relatively high pressure refrigerants. Therefore, a heat exchange device which is suitable for a low pressure refrigerant environment is desired.
Embodiments of the present disclosure are directed to a heat exchange device for a low pressure refrigerant. The heat exchange device includes a first heat exchange unit and a second heat exchange unit. A first refrigerant outlet of the first heat exchange unit is in fluid communication with a first refrigerant inlet of the second heat exchange unit through a throttling device, the first heat exchange unit has a first condenser tube bundle disposed in a first cylinder of the first heat exchange unit, a second cylinder of the second heat exchange unit includes a refrigerant dispenser extending along an axial direction of the second cylinder to form a chamber within the second cylinder having an upper portion and a lower portion, a second condenser tube bundle is disposed in the upper portion of the chamber, and an evaporation tube bundle is disposed in the lower portion of the chamber.
In some embodiments, the first heat exchange unit includes a second refrigerant inlet and the first refrigerant outlet; and the second heat exchange unit includes the first refrigerant inlet and a second refrigerant outlet.
In some embodiments, a first impingement plate is disposed between the first condenser tube bundle of the first heat exchange unit and the second refrigerant inlet; and a second impingement plate is disposed between the second condenser tube bundle of the second heat exchange unit and the first refrigerant inlet.
In some embodiments, a gas-returning liquid baffle is disposed in the second cylinder of the second heat exchange unit and partitions the second cylinder into the chamber and a gas returning chamber along the axial direction of the cylinder, the second refrigerant outlet is in fluid communication with the gas returning chamber, and the first refrigerant inlet is in fluid communication with the chamber.
In some embodiments, the first heat exchange unit further includes first tube plates, a first front water tank, and a first rear water tank that are disposed at first ends of the first cylinder of the first heat exchange unit, the first front water tank is provided with a first inlet and a first outlet, and a first pass partition plate is disposed within the first front water tank to partition the first inlet from the first outlet.
In some embodiments, the second heat exchange unit includes second tube plates, a second front water tank, and a second rear water tank that are disposed at second ends of the second cylinder of the second heat exchange unit, the second front water tank is provided with a second inlet, a chilled fluid inlet, and a chilled fluid outlet, a front water tank partition plate that blocks cooling fluid from mixing with chilled fluid is disposed between the second inlet and the chilled fluid outlet, a second pass partition plate is disposed between the chilled fluid inlet and the chilled fluid outlet, and a rear water tank partition plate that blocks the cooling fluid from mixing with the chilled fluid is disposed within the second rear water tank.
In some embodiments, the second inlet of the second heat exchange unit is in fluid communication with the first inlet of the first heat exchange unit through a conduit, and the second rear water tank of the second heat exchange unit is further provided with a return in fluid communication with the first rear water tank of the first heat exchange unit.
In another aspect, the present disclosure relates to a method for using a heat exchange device that includes receiving a refrigerant vapor discharged from a compressor outlet port in a first cylinder of a first heat exchange unit via a first refrigerant inlet, condensing the refrigerant vapor into a refrigerant liquid after passing the refrigerant vapor over a first condenser tube bundle disposed in the first cylinder of the first heat exchange unit, directing the refrigerant liquid through a first refrigerant outlet of the first heat exchange unit into a connection conduit coupled to a second refrigerant inlet of a second heat exchange unit, receiving the refrigerant liquid in a second cylinder of the second heat exchange unit via the second refrigerant inlet, condensing the refrigerant liquid into a saturated refrigerant liquid after passing the refrigerant liquid over a second condenser tube bundle of the second heat exchange unit, directing the saturated refrigerant liquid through a refrigerant dispenser disposed within the second cylinder of the second heat exchange unit, such that the saturated refrigerant liquid becomes a two-phase refrigerant, and evaporating the two-phase refrigerant into the refrigerant vapor after passing the two-phase refrigerant over an evaporation tube bundles disposed in the second cylinder of the second heat exchange unit.
Embodiments of the present disclosure also relate to a heat exchange device that includes a first heat exchange unit having a first condenser tube bundle and a first impingement plate disposed within a first cylinder of the first heat exchange unit, where the first impingement plate is disposed in the first cylinder proximate to a first refrigerant inlet and a second heat exchange unit having a refrigerant dispenser, a second condenser tube bundle, and an evaporation tube bundle disposed in a second cylinder of the second heat exchange unit, where a first refrigerant outlet of the first heat exchange unit is in fluid communication with a second refrigerant inlet of the second heat exchange unit through a throttling device, and the second impingement plate is disposed in the second cylinder proximate to the second refrigerant inlet.
Embodiments of the present disclosure relate to a double-tube bundle heat exchange device suitable for a low pressure refrigerant, which may have a less complex structure, higher efficiency, and/or reduced refrigerant charge.
A typical falling-film evaporator configured to utilize a relatively high pressure refrigerant (e.g., R134a) may generally include a structure as shown in
The refrigerant dispenser 50 may enhance uniform distribution of the refrigerant onto the evaporation tube bundles 53. However, typical falling-film evaporators may be configured to utilize a relatively high pressure refrigerant (e.g., R134a). Therefore, the refrigerant dispenser 50 may include a pressure difference that accommodates the high pressure refrigerant to ultimately direct the refrigerant over the evaporation tube bundles 53. For example, in some cases, the pressure difference across the refrigerant dispenser may be up to 150 kilopascals (kPa) or up to 300 kPa.
In accordance with embodiments of the present disclosure, the refrigeration system may include a low pressure refrigerant, such as R1233zd(E). Low pressure refrigerants are becoming more desirable because they are generally more environmentally friendly and efficient than high pressure refrigerants. Table 1 shows a comparison between respective evaporation pressures and condensation pressures of R1233zd(E) and R134a under typical refrigeration working conditions (with an evaporation temperature of 5° C. and a condensation temperature of 36.7° C.). As shown, a difference between the evaporation pressure (Pevap, kPA) and the condensation pressure (Pcond, kPa) of R1233zd(E) is 23.1% of the pressure difference of R134a. Accordingly, the refrigerant dispenser 50 may be configured to accommodate the large pressure difference of relatively high pressure refrigerants to distribute the high pressure refrigerants over the evaporation tube bundles 53. However, such a pressure difference may be too high for low pressure refrigerants, such that the refrigerant dispenser 50 may not sufficiently distribute low pressure refrigerant over the evaporation tube bundles 53 (e.g., the low pressure refrigerant may simply fall through the refrigerant dispenser 50 without dispersing towards ends of the refrigerant dispenser 50).
In some embodiments, the liquid baffle 12 may partition an interior of the cylinder 7 into a gas returning chamber 15 and a piping chamber 19 along an axial direction of the cylinder 7. The gas returning chamber 15 may be in fluid communication with the piping chamber 19 through an opening 20 provided at a lower portion of the liquid baffle 12. Further, the second heat exchange unit refrigerant inlet 8 may be in fluid communication with the piping chamber 19 and the second heat exchange unit refrigerant outlet 9 may be in fluid communication with the gas returning chamber 15. As shown in the illustrated embodiment of
Further, the second heat exchange unit 18 may include tube plates 30, a front water tank 31, and a rear water tank 32 that are disposed at ends of the cylinder 7 of the second heat exchange unit 18. The front water tank 31 is provided with a cooling fluid inlet 26, a chilled fluid inlet 27, and a chilled fluid outlet 28. The inlet 26 may be in fluid communication with the inlet 24 of the first heat exchange unit 16 through a conduit 38, which may be in fluid communication with a cooling fluid inlet 29. The second heat exchange unit 18 may further include a partition plate 35 disposed between the inlet 26 and the chilled fluid outlet 28 to block cooling fluid from mixing with chilled fluid in the front water tank 31. Additionally, a pass partition plate 36 may be disposed between the chilled fluid inlet 27 and the chilled fluid outlet 28, such that the chilled fluid may make two passes through the second heat exchange unit 18. A partition plate 37 is disposed inside the rear water tank 32 and also blocks the cooling fluid from mixing with the chilled fluid in the rear water tank 32. The rear water tank 32 is further provided with a cooling fluid return 33, which may be in fluid communication with the rear water tank 23 of the first heat exchange unit 16. Accordingly, cooling fluid that enters the second heat exchange unit 18 may be directed through the first heat exchange unit 16 after passing through the second heat exchange unit 18.
For example, the cooling fluid flowing through the cooling fluid inlet 29 may be divided into two paths via the conduit 38. The first path of the cooling fluid may direct the cooling fluid from the inlet 24, through a first pass of a condenser tube bundle 5 of the first heat exchange unit 16, and into the rear water tank 23 of the first heat exchange unit 16. The first path may then direct the cooling fluid from the rear water tank 23 of the first heat exchange unit 16, through a second pass of the condenser tube bundle 5, and back into the front water tank 22 to the outlet 25. While flowing through the first and second passes of the condenser tube bundle 5, the cooling fluid may be in a heat exchange relationship with another fluid in the cylinder 1.
The second path of the cooling fluid may direct the cooling fluid from the cooling fluid inlet 26, through condenser tube bundle 10 of the second heat exchange unit 18, and into the rear water tank 32. While flowing through the condenser tube bundle 10, the cooling fluid may be in a heat exchange relationship with another fluid in the cylinder 7. Further, the second path may direct the cooling fluid from the rear water tank 32 of the second heat exchange unit 18 into the rear water tank 23 of the first heat exchange unit 16 via the return 33. Accordingly, the cooling fluid that flows through the second heat exchange unit 18 may also flow through the second pass of the condenser tube bundle 5, such that the cooling fluid is also placed in a heat exchange relationship with the fluid in the cylinder 1 of the first heat exchange unit 16 (e.g., after mixing with the cooling fluid flowing through the first heat exchange unit 16 in the rear water tank 23 of the first heat exchange unit 16). The cooling fluid may then be directed into the front water tank 22 of the first heat exchange unit 16 and discharged from the outlet 25.
Additionally, the chilled fluid may enter the front water tank 31 of the second heat exchange unit 18 from the chilled fluid inlet 27. The chilled fluid may then flow through a first pass an evaporation tube bundle 13 and into the rear water tank 32 of the second heat exchange unit 18. Accordingly, the chilled fluid may also be placed in a heat exchange relationship with the fluid in the cylinder 7 of the second heat exchange unit. The chilled fluid may flow from the rear water tank 32 of the second heat exchange unit through a second pass of the evaporation tube bundle 13, into the front water tank 31 of the second heat exchange unit 18, and discharged through the chilled fluid outlet 28.
In the embodiments of
After flowing through the throttling device 6, the medium-pressure, two-phase refrigerant may enter an interior of the cylinder 7 of the second heat exchange unit 18 through a refrigerant inlet 8 of the second heat exchange unit 18. In some embodiments, the impingement plate 11 disposed within the cylinder 7 proximate to the refrigerant inlet 8 may block the medium-pressure, two-phase refrigerant from directly contacting the condenser tube bundle 10 when first introduced into the cylinder 7. Additionally, a cavity may be included between the condenser tube bundle 10 and the refrigerant inlet 8 to facilitate a uniform distribution of the refrigerant around the condenser tube bundle 10. The medium-pressure, two-phase refrigerant may become a medium-pressure, saturated liquid refrigerant after flowing through the condenser tube bundle 10. For example, the medium-pressure, two-phase refrigerant may condense upon transferring heat to the cooling fluid flowing through the condenser tube bundle 10. The medium-pressure, saturated liquid refrigerant may then uniformly drip onto the refrigerant dispenser 14.
In some embodiments, a difference between enthalpy of the refrigerant upstream of the condenser tube bundle 10 and the refrigerant downstream of the condenser tube bundle 10 may be expressed as DH=h1′−h1, where DH is the enthalpy difference, h1′ is the enthalpy of the refrigerant upstream of the condenser tube bundle 10 and h1 is the enthalpy of the refrigerant downstream of the condenser tube bundle 10 (see, e.g.,
In any case, the medium-pressure, saturated liquid refrigerant may become a low-pressure, two-phase refrigerant after passing through the refrigerant dispenser 14 as a result of further pressure reduction of the refrigerant as it passes through the refrigerant dispenser 14. For example, a difference between the pressure (DP2) of the refrigerant upstream of the refrigerant dispenser 14 (P1) and downstream of the refrigerant dispenser 14 (Pe) and after the refrigerant dispenser is DP2=P1−Pe (see, e.g.,
Further, the second heat exchange unit 18 further includes the tube plates 30, the front water tank 31, and the rear water tank 32 that are disposed at the ends of the cylinder 7 of the second heat exchange unit 18. The front water tank 31 is provided with two inlets 39 and a chilled fluid outlet 28. As shown in the illustrated embodiment of
The chilled fluid flowing through the chilled fluid inlet 40 is divided into two paths through the conduit 38. The first path of the chilled fluid may direct the chilled fluid into the front water tank 31 from the first inlet 39, through the condenser tube bundle 10 of the second heat exchange unit 18, and into the rear water tank 32. Accordingly, the chilled fluid may be placed in heat exchange relationship with the refrigerant flowing through the cylinder 7 of the second heat exchange unit 18.
The second path of the chilled fluid may direct the chilled fluid into the front water tank 31 from the second inlet 39, through a first pass of the evaporation tube bundle 13, and into the rear water tank 32. Therefore, the chilled fluid of the second path may also be placed in a heat exchange relationship with the refrigerant flowing through the cylinder 7. In the rear water tank 32, the chilled fluid from the condenser tube bundle 10 and the first pass of the evaporation tube bundle 13 may combine with one another. The combined chilled fluid may then flow from the rear water tank 32, through a second pass of the evaporation tube bundle 13, into the front water tank 31, and is discharged through the chilled fluid outlet 28.
The cooling fluid enters the front water tank 22 of the first heat exchange unit 16 from the inlet 24, flows through a first pass of the condenser tube bundle 5, and into the rear water tank 23 of the first heat exchange unit 16. Accordingly, the cooling fluid is placed in a heat exchange relationship with the refrigerant within the cylinder 1 of the first heat exchange unit 15. The cooling fluid in the rear water tank 23 is then directed into a second pass of the condenser tube bundle 5, into the front water tank 22, and discharged through the outlet 25. The cooling fluid is then placed in another heat exchange relationship with the refrigerant in the cylinder 1 when flowing through the second pass of the condenser tube bundle 5.
In the embodiments of
After flowing through the throttling device 6, the medium-pressure, two-phase refrigerant may enter an interior of the cylinder 7 of the second heat exchange unit 18 through a refrigerant inlet 8 of the second heat exchange unit 18. In some embodiments, the impingement plate 11 disposed within the cylinder 7 proximate to the refrigerant inlet 8 may block the medium-pressure, two-phase refrigerant from directly contacting the condenser tube bundle 10 when first introduced into the cylinder 7. Additionally, a cavity may be included between the condenser tube bundle 10 and the refrigerant inlet 8 to facilitate a uniform distribution of the refrigerant around the condenser tube bundle 10. The medium-pressure, two-phase refrigerant may become a medium-pressure, saturated liquid refrigerant after flowing over the condenser tube bundle 10. For example, the medium-pressure, two-phase refrigerant may condense upon transferring heat to the chilled fluid flowing through the condenser tube bundle 10. The medium-pressure, saturated liquid refrigerant may then uniformly drip onto the refrigerant dispenser 14.
In some embodiments, a difference between enthalpy of the refrigerant upstream of the condenser tube bundle 10 and the refrigerant downstream of the condenser tube bundle 10 may be expressed as DH_2=h1′−h1_2, where DH_2 is the enthalpy difference, h1′ is the enthalpy of the refrigerant upstream of the condenser tube bundle 10 and h1_2 is the enthalpy of the refrigerant downstream of the condenser tube bundle 10 (see, e.g.,
In any case, the medium-pressure, saturated liquid refrigerant may become a low-pressure, two-phase refrigerant after passing through the refrigerant dispenser 14 as a result of further pressure reduction of the refrigerant as it passes through the refrigerant dispenser 14. For example, a difference between the pressure (DP2_2) of the refrigerant upstream of the refrigerant dispenser 14 (P1_2) and downstream of the refrigerant dispenser 14 (Pe) and after the refrigerant dispenser is DP2_2=P1_2−Pe (see, e.g.,
Compared with the embodiment illustrated in
While only certain features and embodiments have been illustrated and described, many modifications and changes may occur to those skilled in the art (e.g., variations in sizes, dimensions, structures, shapes and proportions of the various elements, values of parameters (e.g., temperatures, pressures, etc.), mounting arrangements, use of materials, colors, orientations, etc.) without materially departing from the novel teachings and advantages of the subject matter recited in the claims. The order or sequence of any process or method steps may be varied or re-sequenced according to alternative embodiments. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the disclosure. Furthermore, in an effort to provide a concise description of the exemplary embodiments, all features of an actual implementation may not have been described (i.e., those unrelated to the presently contemplated best mode of carrying out the embodiments of the present disclosure, or those unrelated to enabling the claimed disclosure). It should be appreciated that in the development of any such actual implementation, as in any engineering or design project, numerous implementation specific decisions may be made. Such a development effort might be complex and time consuming, but would nevertheless be a routine undertaking of design, fabrication, and manufacture for those of ordinary skill having the benefit of this disclosure, without undue experimentation.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2016 1 0095118 | Feb 2016 | CN | national |
| 2016 2 0131265 U | Feb 2016 | CN | national |
| Number | Name | Date | Kind |
|---|---|---|---|
| 20090178789 | Luo | Jul 2009 | A1 |
| 20090242178 | Al-Anizi | Oct 2009 | A1 |
| 20130277018 | Numata | Oct 2013 | A1 |
| 20150007604 | Hu | Jan 2015 | A1 |
| Number | Date | Country | |
|---|---|---|---|
| 20170241682 A1 | Aug 2017 | US |
