STRUCTURE FOR THE END OF PRESSURE VESSELS, MOST APPLICABLY PLATE HEAT EXCHANGERS, FOR REDUCING THE EFFECTS OF MOVEMENT CHANGES AND VIBRATIONS CAUSED BY VARIATIONS IN INTERNAL PRESSURE AND TEMPERATURE, A METHOD FOR IMPLEMENTING IT AND USE OF SAME

Abstract

A structure for the end of pressure vessels, most applicably plate heat exchangers, for reducing the effects of movement changes and vibrations caused by variations in internal pressure and temperature. The end is made up of a heat transfer plate and an end part in such a way that the end part is connected by welding to the shell of the outer surface of the heat exchanger stack, forming an enclosed chamber on the end of the heat exchanger, into which chamber higher pressure than the external pressure level is brought and/or generated. The higher pressure receives and dampens, via a heat transfer plate, vibration and pressure shocks harmful to the heat exchanger structure in the medium circuits of the heat exchanger.

Claims

1. A structure for the end of pressure vessels, most applicably plate heat exchangers, for reducing the effects of movement changes and vibration caused by variations in internal pressure and temperature, wherein the end is made up of a sheet metal heat transfer plate and an end part in such a way that the end part is connected by welding to the shell of the outer surface of the heat exchanger stack, forming an enclosed chamber on the end of the heat exchanger, into which chamber higher pressure than the external pressure level is brought and/or generated, which higher pressure receives and dampens, via a heat transfer plate, vibration and pressure shocks harmful to the heat exchanger structure inside the medium circuits of the heat exchanger.

2. Structure according to claim 1, wherein inside the end part is fitted a reinforcing plate, detached from the end part and filling the chamber as well as possible, in such a way that the last sheet metal heat transfer plate of the heat exchanger stack rests as tightly as possible against the reinforcing plate, in such a way that a pressure load being exerted on the heat transfer plates is transmitted via the edges of the reinforcing plate to the end part as almost purely a tensile stress load.

3. Structure according to claim 1, wherein on both ends of the heat exchanger is an enclosed chamber which is a free volume definable according to the size of the end part and heat transfer plate, reduced by the volume of the reinforcing plate, in such a way that it is connected to the rest of the heat exchanger stack bounded by a thin, flexible and drumhead-like sheet metal heat transfer plate.

4. Structure according to claim 1, wherein the enclosed chamber is a pressure chamber, to the inside of which is brought gas pressure by means of a valve or in some other manner via a closable hole, e.g. in such a way that via the hole internal gas pressure preselected to be appropriate to the operating situation is brought in conjunction with the manufacture of the end structure, and it is closed immediately to be leak-tight.

5. Structure according to claim 1, wherein the enclosed chamber is a pressure chamber, to the inside of which is brought a medium, most suitably water, ammonia-water, ammonia, carbon dioxide, air, and by means of a rise in the temperature of the medium an internal gas pressure appropriate to the operating situation is generated.

6. Structure according to claim 5, wherein the pressure of the enclosed chamber is defined according to the volume of the chamber and the saturated vapor pressure of the amount of vaporizable fluid of the medium selected for the chamber, when the temperature exceeds the vaporization pressure.

7. Method for reducing the effects of movement changes and vibrations caused by variations in internal pressure and temperature of pressure vessels, most applicably plate heat exchangers, wherein into the enclosed chamber formed on the end of the heat exchanger is brought and/or generated a higher pressure than the external pressure level, which higher pressure receives and dampens, via a heat transfer plate, vibration and pressure shocks harmful to the heat exchanger structure in the medium circuits of the heat exchanger.

8. Method according to claim 7, wherein the enclosed chamber is a pressure chamber, to the inside of which is brought gas pressure by means of a valve or in some other manner via a closable hole, e.g. in such a way that via the hole internal gas pressure preselected to be appropriate to the operating situation is brought in conjunction with the manufacture of the end structure, and it is closed immediately, e.g. by welding, to be leak-tight.

9. Method according to claim 7, wherein to the inside of the enclosed pressure chambers of both ends of the heat exchanger is brought a medium, which is most suitably water, ammonia-water, ammonia, carbon dioxide, air, and by means of a rise in the temperature of the medium an internal gas pressure appropriate to the operating situation is generated.

10. Method according to claim 9, wherein the pressure of the enclosed chamber is defined according to the volume of the chamber and the saturated vapor pressure of the amount of vaporizable fluid of the medium selected for the chamber, when the temperature exceeds the vaporization pressure.

11. Use of the enclosed chamber formed on the end of a heat exchanger, into which chamber higher pressure than the external pressure level is brought and/or generated, which higher pressure receives and dampens, via a heat transfer plate, vibration and pressure shocks harmful to the heat exchanger structure in the medium circuits of the heat exchanger.

12. Use according to claim 11, wherein the enclosed chamber formed at both ends of the heat exchanger is used as a pressure chamber, to the inside of which is brought a gas pressure higher than the external pressure level by means of a valve or in some other manner via a closable hole, or to the inside of which is brought a medium, most suitably water, ammonia-water, ammonia, carbon dioxide, air, and by means of a rise in the temperature of the medium, occurring by conducting the mediums used in transferring heat, an internal gas pressure appropriate to the operating situation is generated in the chamber.

13. Structure according to claim 2, wherein on both ends of the heat exchanger is an enclosed chamber which is a free volume definable according to the size of the end part and heat transfer plate, reduced by the volume of the reinforcing plate, in such a way that it is connected to the rest of the heat exchanger stack bounded by a thin, flexible and drumhead-like sheet metal heat transfer plate.

14. Structure according to claim 3, wherein the enclosed chamber is a pressure chamber, to the inside of which is brought gas pressure by means of a valve or in some other manner via a closable hole, e.g. in such a way that via the hole internal gas pressure preselected to be appropriate to the operating situation is brought in conjunction with the manufacture of the end structure, and it is closed immediately to be leak-tight.

15. Structure according to claim 3, wherein the enclosed chamber is a pressure chamber, to the inside of which is brought a medium, most suitably water, ammonia-water, ammonia, carbon dioxide, air, and by means of a rise in the temperature of the medium an internal gas pressure appropriate to the operating situation is generated.

16. Method according to claim 8, wherein to the inside of the enclosed pressure chambers of both ends of the heat exchanger is brought a medium, which is most suitably water, ammonia-water, ammonia, carbon dioxide, air, and by means of a rise in the temperature of the medium an internal gas pressure appropriate to the operating situation is generated.

Description

BRIEF DESCRIPTION OF THE FIGURES

[0021] In the following, the invention will be described in more detail by the aid of an example of its embodiment with reference to the attached drawings 1-2, wherein:

[0022] FIG. 1 presents a preferred embodiment of the invention, in which the parts essential to the invention are presented disassembled.

[0023] FIG. 2 presents a preferred embodiment of the invention, in which the parts essential to the invention are presented when assembled.

DETAILED DESCRIPTION OF THE INVENTION

[0024] The realization of the present invention is most preferably deployable and applicable in the structure of a heat exchanger, which is disclosed e.g. in patent EP0375691 (FI 79409) and in specification EP-1163968 (US20000253) supplementing said patent. The specification shows more particularly the structure of the ends of a heat exchanger, in which structure the invention is most clearly applicable.

[0025] One preferred solution of the invention is presentable by way of illustration as applied to the aforementioned structure. The heat exchanger in specification EP-1163968 (US20000253) is made up of thin, usually stainless steel, 0.4-0.7 mm thick heat transfer plates 1, usually 3 mm thick end parts 3, and narrow joining parts 2 of the thickness of the plate interspace on the edges of the heat transfer plates. The purpose of the joining part 2 is to fit, fasten and seal the heat transfer plates into an integral welded structure on the outer edge. A heat exchanger is formed from the heat transfer plates 1 and the joining parts 2 when piling them one on top of another. It is provided, by welded sealing, with separated chambers formed from alternate plate interspaces, i.e. medium circuits, for heat transfer. A sealed and compact heat exchanger stack 8 is formed, the outer surface of which is welded into an integral shell into which, by means of the joining parts 2, i.e. by opening them applicably, are made inlet and outlet flow apertures into the alternate plate interspaces of the medium circuits.

[0026] FIGS. 1 and 2 present in a simplified manner the most important parts from the standpoint of the present invention. Most essential is the structure of the ends receiving the internal pressure of the heat exchanger. The ends are built up from parts: a cup-shaped end part 3 and a rigid reinforcing plate 4 fitted as precisely as possible inside the end part 3, although detached from it. The end part 3 is joined by welding to the heat exchanger outer shell described above. In this case the last heat transfer plate of the heat exchanger stack is placed as tightly as possible to rest against the reinforcing plate 4. In this structure the pressure load being exerted on the flexible, drumhead-like, thin heat transfer plates 1 in the end inside the heat exchanger is transmitted via the reinforcing plate 4 and its edges to the end part 3. The load exerted on the end part 3 is almost purely tension and, that being the case, the whole structure has good endurance.

[0027] An enclosed chamber 5 is formed on both ends of the heat exchanger from the end structure presented above. Thus one heat exchanger is provided with two, most preferably two, chambers 5, one at each end of the heat exchanger. What is also essential is that the chamber 5 has a definable free volume, reduced by the volume of the reinforcing plate 4, which free volume joins as described above to the rest of the heat exchanger stack 8 bounded by a thin, flexible and drumhead-like heat transfer plate 1.

[0028] According to the present invention, higher pressure than the external pressure level is brought into or generated in the chamber 5, the purpose of which higher pressure is to receive and dampen vibration, inside the medium circuit of the heat exchanger for various reasons and harmful to the heat exchanger structure, and pressure shocks.

[0029] This structure is useful and possible to implement because the actual operating pressure of the pressure vessel of a heat exchanger is always lower than the test pressure plus safety factors and the corresponding maximum operating pressure permitted by pressure vessel regulations. Furthermore, it is also very possible to make the heat exchanger structure described above significantly exceed these pressure requirements in terms of its strength.

[0030] The enclosed chambers 5 of the end parts of the heat exchanger thus function in such a way that when the operating pressure is e.g. 4 bar, which is very usual in systems utilizing steam, an internal gas pressure of 4-6 bar is brought into or generated in the chambers 5 to receive harmful vibration and pressure shocks. If, for one reason or another, the pressure inside the heat exchanger is higher than the pressure in the chambers 5, the reinforcing plate 4 in the structure according to specification EP-1163968 (US20000253) starts to receive the load caused by the pressure. In this situation the strength of the structure corresponds to the pressure vessel requirement set for it and in most cases exceeds it.

[0031] Internal gas pressure suited to the operating situation is brought into the chambers 5 on the ends of the heat exchanger by means of a valve or in some other manner via a closable hole 6. The enclosed chamber 5 functions as a pressure chamber, to the inside of which is brought pressure 7 by means of a valve or in some other manner via a closable hole 6, e.g. in such a way that via the hole 6 internal gas pressure 7 preselected to be appropriate to the operating situation is brought in conjunction with the manufacture of the end structure, and it is closed immediately to be leak-tight.

[0032] 15

[0033] It is advantageous, according to this invention, to generate inside the chambers 5 an internal gas pressure 7 applicable to the operating situation by effect of the temperature from the mediums and by heat conducted into the chamber 5. This occurs by defining the free volume of the chamber 5. Fluid that is vaporizable from the effect of temperature is brought into and enclosed in the chamber 5, the amount of the fluid being proportional to the free volume of the chamber 5. The pressure of the chamber 5 is defined according to the saturated vapor pressure of the amount of vaporizable liquid when the temperature exceeds the vaporization pressure. When the amount of vaporizable liquid has fully vaporized, the pressure does not rise significantly when the temperature rises and the steam superheats.

Water Embodiment

[0034] Characteristic to the invention are the enclosed chambers 5, which are connected via thin and flexible heat transfer plates 1 to the rest of the heat exchanger stack.

[0035] First, the free volume of the chamber 5 is determined, which is e.g. 1 dl. The mediums and the steam heat the chamber 5 to a temperature of 143° C. The density of the saturated water vapor at a temperature of 143° C. and a pressure of 4 bar is 2.16 kg/m3. If a pressure corresponding to an operating pressure of 4 bar is desired in the enclosed chamber 5, which has a volume of 1 dl, 0.216 ml of water must be brought into it. Thus the magnitude of the pressure in the chamber 5 can be specified by means of the amount of water brought into it.

[0036] What is essential to the invention is that the pressure does not rise much above this, even if the temperature of the chamber 5 were to rise significantly. A temperature of e.g. 200° C. is selected. It is seen that when the water vapor becomes superheated, the pressure is 4.6 bar. The pressure level of the chamber 5 has thus not risen much at all. If a temperature of 200° C. and an adequate amount of water required for saturated steam were brought into the chamber 5, the pressure would be 15.5 bar.

[0037] From the above, it can be seen that with the preconditions according to the embodiment a sufficiently controllable internal pressure can be generated in the chamber 5 for dampening the pressure shocks and vibration of a heat exchanger that are caused by pressure.

Ammonia-water Embodiment

[0038] Very often the temperature of heat exchanger mediums is below 100° C., in which case according to the embodiment presented above there is no advantage in bringing water into the chamber 5.

[0039] A very good and practicable vaporizable liquid at a temperature below 100° C. is ammonia-water. For example, when 25% ammonia-water vaporizes at a temperature of approx. 50° C., a pressure of 3-4 bar is produced before it superheats.

Carbon Dioxide or Ammonia Embodiments

[0040] The corresponding embodiments for carbon dioxide and for ammonia according to what is presented above.

[0041] Carbon Dioxide Embodiment:

Saturated vapor −28.8° C., in which case the pressure is 15 bar.
Superheated amount of vaporizable mass according to the embodiment at a temperature of +50° C., in which case the pressure is 21.7 bar.

[0042] If the amount of mass is increased sufficiently, the pressure at a temperature of +50° C. is 73.8 bar.

[0043] Ammonia Embodiment:

Saturated vapor 38.8° C., in which case the pressure is 15 bar.
Superheated amount of vaporizable mass according to the embodiment at a temperature of +110° C., in which case the pressure is 19.9 bar.

[0044] If the amount of mass is increased sufficiently, the pressure at a temperature of +110° C. is 75.7 bar.

Air Embodiment

[0045] One example of gases worth mentioning is air, which is pressurized in the enclosed space 5 to a pressure of 5 bar when the temperature is 25° C. When the temperature rises to 300° C., the pressure of the gas has risen to only 9.7 bar.

[0046] Presented above by way of illustration are some vaporizable liquids and gases suited to an application of the invention.

[0047] Essential to the invention is the use of the enclosed chamber 5 formed on the end of a heat exchanger. Accordingly to what is presented above, the chamber 5 is used in the method according to the invention in such a way that a higher pressure 7 than the external pressure level, is brought into and/or generated in the enclosed chamber 5 formed on the end of the heat exchanger, which higher pressure receives and dampens, via a heat transfer plate 1, vibration and pressure shocks harmful to the heat exchanger structure in the medium circuits of the heat exchanger. Particularly essential to the invention is the design of the end, such that the end is constructed from a heat transfer plate 1 and an end part 3, in such a way that the end part 3 is connected by welding to the shell of the outer surface of the heat exchanger stack 8, forming an enclosed chamber 5 on the end of the heat exchanger. In addition to this, into the enclosed chamber 5, inside the end part 3, is fitted a rigid reinforcing plate 4 receiving internal pressure, the reinforcing plate although detached from the end part 3 filling the chamber 5 as well as possible.

[0048] It is obvious to the person skilled in the art that the different embodiments of the invention are not limited solely to the examples described above, but that they may be varied within the scope of the claims presented below.