JPH02238255A - Method and device for controlling refrigerant load through detection of refrigerant temperature - Google Patents

Abstract

PURPOSE: To perform more accurate superheat control by providing an inlet, an outlet, and an internal conduction passage of refrigerant, providing a heat conducting material at least on a part of the wall of the passage and detecting inner temperature through the wall part. CONSTITUTION: The apparatus 48 is made of a highly conductive material and provided with a first inner tubular pipe 62 having one end formed with a flange for constituting a flow-in port 46 and the other closed end 64. A second large diameter outer tubular pipe 66 surrounds the first inner pipe coaxially. The inner pipe is filled with a spiral coil 67 made of an open mesh material and provided with a plurality of holes 68 arranged uniformly along the length and circumferential edge of the pipe. Refrigerant vapor and liquid flowing in through the flow-in port 46 is delivered forcibly to the inner wall of the outer pipe 66. Refrigerant flows are mixed by combining turbulences in an annular chamber 70 between two pipes and thereby different temperatures are averaged entirely and an evaporation valve is controlled according to the detected temperature.

Description

Detailed Description of the Invention [Industrial field in Icheon] The present invention provides a method and device for detecting refrigerant temperature in a refrigeration system, and particularly a method and device for controlling refrigerant fL{i7 in an evaporator of a refrigeration system Vi. Regarding. BACKGROUND OF THE INVENTION A typical compressor-operated refrigeration system consists of a closed circuit in which low-temperature, low-pressure refrigerant vapor from a suction line enters the compressor, where it enters a high-temperature Compressed to high pressure vapor, this hot vapor then flows through a discharge line into one or more condensing coils where it is cooled below its condensing temperature and turned into a liquid. This liquid flows from the condenser via a return line into a liquid receiver, and from the receiver via a liquid line to the display device and filter/dryer, from where it is thermostatically maintained at an optimum value. Directed to the expansion valve, this liquid refrigerant stream is directed to one or more evaporator coils where it is evaporated, resulting in a temperature drop and cooling of the coils and their surrounding environment, and the resulting vapor is passed through the suction line. The circuit is then completed by returning to the compressor. Any liquid refrigerant can be damaged by pressure IIIa
The expansion valve (usually
It is important to control the
Typically, the control of this valve consists of a remote temperature sensing fluid-containing sphere connected by a metal capillary to the valve's loaded diaphragm capsule. The capsule adjusts the flow through the valve in response to changes in the temperature of the sensing sphere. Equivalent electrical sensors have also been developed. A sensor sphere or equivalent is typically clamped tightly to the suction line at the outlet from the discharge manifold into which the evaporator coil or coils discharge, so as to detect the temperature of the fume air at this point. It has become. The temperature characteristics of liquid evaporators are quite standard, i.e. their temperature is relatively constant around their respective evaporation (saturation) temperature as long as there is some liquid to evaporate; When liquid is lost, it rises relatively quickly. To ensure that no liquid leaks from the evaporator, the sensor is set at an operating temperature well above the saturation temperature, and the difference between these two temperatures is known as superheat. As an example, a very common temperature range for saturation temperature for this type of system is about -7°C to about 4.5°C (20"F to 40°F); The control temperature range is -
t°C to lO°C (30°F to 50”F).

Theoretically, even lower superheat values, e.g. 1°C (2″
'F), but in conventional embodiments this condition has been found to be insufficient to ensure that liquid refrigerant is completely absent from the evaporator manifold outlet. , so higher values are generally used.

As the superheat value changes around a predetermined amount, the TX valve opens and closes and, in theory, should operate to maintain it very accurately at that value, but in reality, the sensor detects the temperature. and the actuation of the TX valve, and also usually cannot respond fast enough, resulting in varying superheat values, necessitating higher values; The efficiency of the system is therefore reduced. Therefore, there is a continuing need for a temperature sensor for this type of system that can more accurately determine (measure) the temperature of the refrigerant vapor in the suction line, thereby improving efficiency. In commercial refrigerators, there are many evaporators, often 50
consisting of separate "circuit coils" that are connected in parallel to provide sufficient cooling without the individual coils having too much length and resulting in high pressure drops. The capacity has been achieved. These circuit coils are comprised of sets, each set having its own expansion valve and a common distributor interposed between the valves of the set and the coils;
The purpose of this distributor is to divide the flow as equally as possible between individual small diameter supply pipes of equal length leading from the distributor to the pipe inlet of each circuit coil. All circuit coil pipe outlets are connected to a common outlet manifold or standpipe. Despite the fact that valves and distributors ensure that equal amounts of liquid refrigerant are delivered to the circuit coils, and that all circuit coils are as similar in length and flow characteristics as possible, in practice there is a variation in the number of It has been observed that, for example, due to differences in air flow rates passing over different coils, and small differences in pressure drop values across each coil, the liquid chilled tofu evaporates at a different rate in one coil than in another. . As a result, j11 absorbs the least amount of ambient heat.
- or multiple circuit coils allow the liquid refrigerant to flow further along itself to facilitate evaporation, such that these single or multiple coils control the TX valve and shut it off; As a result, the remaining coils are starved of liquid refrigerant, and the refrigerant vapor in the starved coils is overheated, thus reducing the cooling capacity of the system. This reduction amounts to about 25-35% of the total capacity.

This unequal loading of the evaporator circuit coils typically occurs when the system is operated for short periods of time when the deficient circuit coils are less frosted toward the outlet end than in the other direction. It can be observed by visual inspection. This unequal loading often erroneously results in unequal distribution of refrigerant liquid along the coils.
U.S. Pat. No. 3,555.845 and U.S. Pat.
No. 740.967 S (both Danfoss A/S, Denmark) discloses a forced flow evaporator for a compression refrigeration system in which a A subsequent tube has its inner wall lined with gauge fibers to provide a capillary system for absorbing liquid refrigerant, the gauge fibers occupying less than half the cross-sectional area of the tube and thus substantially A central passage is left through which the vapor passes at high speed without mixing with the liquid held in the gauge tam, which has the effect of forming a relatively stagnant layer on the tube wall. become. U.S. Pat. No. 4,229,949 (Stal Refrigeration AB, Sweden) discloses a refrigeration system in which a flow obstruction element is disposed in the suction pipe downstream of the evaporator; It operates on the fluid in the pipe and imparts an increased relative velocity to the two phase forms found therein, namely liquid particles and superheated vapor, increasing the rate of heat transfer between them. increased to ensure that the refrigerant exits only in the vapor phase. This element consists of a disc with an opening, which is arranged perpendicular to the direction of flow of the coolant and is designed to generate turbulence to accelerate temperature equalization. OBJECTS OF THE INVENTION Therefore, the main object of the present invention is to provide a novel method and apparatus for detecting refrigerant temperature in a refrigeration system, and in particular to efficiently detect the temperature of refrigerant exiting an evaporator coil by means of a temperature sensor controlling a TX valve. The object of the present invention is to provide a new method and device for more accurate superheat control. Another object is to provide a new method and apparatus for controlling the refrigerant load in the evaporator coil of a refrigeration system. [Means for Solving the Problems] In the present invention, the temperature of the refrigerant flowing out from the discharge port of the evaporator coil of the refrigeration system is detected, and according to this detected temperature, the controllable refrigerant is supplied to the inlet of the evaporator coil. A method is provided for controlling an evaporator valve, the method providing refrigerant from a coil outlet into an interior of a turbulence and mixing device, providing a refrigerant flow passageway in the device, and providing at least one wall of the device with a refrigerant flow passage. A part of the wall has a thermally conductive material so that the internal temperature of the device can be detected through this wall part; a turbulence and mixing generating device, i.e. preventing the total refrigerant flow;
and changing the direction of the total refrigerant flow to ensure turbulence and mixing of all liquid and vapor refrigerant phases present in the refrigerant flow and that only the mixed phase contacts the wall portion. generating turbulent flow and mixing of the refrigerant in the flow passage by a mixing generator; and detecting the internal temperature of the device at the wall portion by a temperature sensing device, and controlling the evaporator valve according to the detected temperature. ing. The present invention also provides a device that detects the temperature of refrigerant flowing out from an evaporator coil outlet of a refrigeration system and controls a controllable evaporator valve that supplies liquid refrigerant to an evaporator coil inlet in accordance with the detected temperature. The device is a turbulent flow and mixing device having an inlet and an outlet for the refrigerant, an internal refrigerant flow passage, and at least a portion of the wall thereof having a thermally conductive material. and a turbulent flow and mixing device configured to detect the internal temperature of the device through its wall portion; provided in the flow path to prevent the total refrigerant flow and to prevent the turbulent flow of the refrigerant by changing the direction of the total refrigerant flow. and a turbulence and mixing generating device for producing turbulence and mixing of all liquid and vapor refrigerant phases present therein and ensuring that only the mixed phases contact the wall portion; a device adapted to detect an internal temperature of the device in thermally conductive contact with a temperature sensing device of the device and to control an evaporator valve in accordance with the detected temperature.

Furthermore, in this invention, is it possible to control the refrigerant load on the evaporator coil of the refrigeration system? 11, a novel method is provided in which evaporator coils are connected in parallel with each other and constrained by a thermoscant. The superheat temperature is comprised of multiple circuit coils all supplied with refrigerant through a common refrigerant flow control valve and refrigerant distributor, which is operated at In a device in which the refrigerant flow rate is controlled by a sensor to limit 1B, the refrigerant flow from the circuit coil is mixed by turbulence and a mixing device and exists at or before the temperature is detected by the Jansa. It is characterized by using a superheated vapor phase refrigerant to vaporize the existing liquid phase refrigerant and average the flow temperature. Further, in the present invention, an apparatus for use in a refrigeration system is provided, which apparatus comprises: a refrigerant compressor; a condensing coil that receives refrigerant from the compressor and cools it; a thermostat that receives cooled refrigerant from the condensing coil. A common refrigerant flow control valve to be controlled; An evaporator coil consisting of a plurality of circuit coils connected in parallel to each other and all supplied with refrigerant from a common control valve; Having an inlet and an outlet. together with a common member that receives the refrigerant flowing out from all the circuit coils; a compressor, a condensing coil, a common control valve, a repulsion coil, a common member inlet, a common member outlet, and a compressor in a closed loop in this order. a connecting conduit arrangement; a superheat temperature sensor operatively connected thereto for detecting refrigerant at the common member outlet and controlling the control valve; The apparatus includes the turbulence and mixing device that generates turbulence and mixes the refrigerant flow, and a temperature detection device that detects the internal temperature of the device. DESCRIPTION OF THE PREFERRED EMBODIMENTS The method and apparatus of the present invention will be illustrated by way of example in the drawings, in which identical or similar parts are numbered the same.

Referring to FIG. 1, a typical refrigeration system in which the method and apparatus of the present invention may be applied includes a refrigerant compressor 10 having a suction inlet 12 and a high pressure outlet 14, which compresses a compressed hot refrigerant fluid. is fed via conduit 15 to a condensing coil 16 having an inlet 18 and an outlet 20. The cooled refrigerant from coil l6 is passed via conduit 21 to a liquid accumulator 22 and then via conduit 24 to a filter/dryer 26, a liquid indicator 28 and a common refrigerant flow control 4 controlled by a thermostat.
1TX valve 30 to a distribution device 32 and from there into two parallel connected circuit coils 34a and 34b of the evaporator coil. For convenience of illustration, only two circuit coils are shown, but in reality, a single large evaporator coil could have as many as 50 circuit coils, each coil connected to each inlet pipe 36a and 36b to the common distribution device 32. In fact, all circuit coils 34a, 34b . ···etc,
and all pipes 36a. 36b, etc. are formed as equally long as possible so that the refrigerant is distributed as equally as possible to them. Each circuit coil has an inlet port 38a, 38b, and a discharge port, respectively. It has outlets 40a, 40b, the latter all connected to a common goose pipe 42 (sometimes called a standpipe or manifold), the single outlet 44 of which is connected to the inlet 46 of the turbulence generating and mixing device 48 of the present invention. connected to. The superheat temperature detection sphere 50, by which the TX valve 30 is controlled, is tightly clamped to the outside of the device 48 by a clamp 51 to ensure good heat exchange with its interior. valve 30 by means of the cabillary tube 52.
is connected to. The outlet 54 of the device 48 is connected to the pump inlet 12 by a conduit 56 to complete the system circuit. Conventional fans 58 and 60 direct ambient air to coils 16 and 34a.., respectively. 34b for circulation. The many other circuit elements, controls and displays that such systems typically include do not form part of this invention and therefore need not be described. The flow direction of the refrigerant is indicated by a dashed arrow. Referring also to FIG. 2, this particular device 48 is formed from a highly conductive material, such as copper or brass, and
A first internal cylindrical pipe 62 is provided, one end of which is flanged to define the inlet 46, and the other end 64 is closed. A second large diameter outer cylindrical pipe 66 surrounds the first inner pipe coaxially therewith and is sealed to the pipe at the end adjacent the inlet 46 and is flanged at the other end to provide a discharge outlet. It constitutes an exit 54.

The interior of the inner pipe is filled with a spirally wound coil 67 of stainless steel open mesh material. The internal pipe includes a plurality of holes 68 that are uniformly distributed along the length and circumference of the pipe and that direct refrigerant vapor and entrained liquid from the inlet 46 to the external pipe 66. The signal is forcibly emitted against the inner wall of the wall. Therefore, the pipes and holes provide variable direction flow paths within the device between the inlet and the outlet, i.e. the numerous tortuous paths formed by the menosh coils 67, the sudden direction of the fast flowing fluid. The combination of changes, turbulence in the inner pipe 62 due to the fluid impinging on the closed end, and turbulence in the annular chamber 70 between the two pipes due to impingement against the inner wall of the outer pipe causes the flow to All refrigerant flows in the path, whether in liquid or vapor phase, are thoroughly mixed and turbulent, and in particular, the relatively high velocity vapor phase is separated from the liquid phase. This can prevent the possibility of fluid flowing through the device. Furthermore, the forceful impingement of the high-velocity fluid against the inner wall of the external pipe destroys the relatively stagnant barrier layer consisting of the refrigerant or the lubricating oil that is always entrained in it, and removes it from the inner wall, thereby removing the refrigerant. Efficient transfer of heat to the sensor sphere 50 through the wall is not impeded. Therefore, the sphere detects only the temperature of the completely turbulent mixed and temperature-averaged refrigerant flow received from the outlet of the hesogoo pipe 42, and is also extremely sensitive to changes in refrigerant temperature. and accurately measure the internal temperature of the device corresponding to the averaged refrigerant temperature. This turbulence generation and mixing function of device 48 is thus effective no matter what configuration of evaporator coil is utilized in the system. When this device is used in the systems specifically described herein, i.e., those with multiple circuit coils, in addition to turbulently mixing the fluid flow in each evaporator circuit coil, it performs a number of mixing functions. and thus the fluid flows from all circuit coils are thoroughly mixed with each other,
All of the separate temperatures are therefore averaged and this average circuit coil temperature is detected by the sphere 50. Furthermore, due to this complete turbulence and mixing, even if a single or multiple circuit coil does not evaporate all of its supplied refrigerant, the small amount of liquid that reaches the mixing device is immediately atomized, resulting in , is easily evaporated by the heat obtained from the superheated steam from the remaining coils. Therefore, the refrigerant supply to the underloaded coil or coils is increased, and eventually the generated superheated vapor evaporates the liquid refrigerant from the underloaded coil or coils. It becomes impossible to do anything. The diameters of pipes 62 and 66 are configured such that the flow capacity of the resulting flow passage is approximately that of the remainder of suction tube 56, and the number and size of openings 68 are such that the flow capacity of the resulting flow passage is approximately the same as that of the remainder of suction tube 56. Configure it so that it is achieved. These flow capacities can vary from about 0.5 to 1.5 times the normal flow capacity of the suction tube, where they are sufficiently forced to impinge on the fluid against the inner wall of the outer tube. Preferably, the flow capacity of opening 68 is reduced to somewhat less than that of the suction tube. Approximately 3-511. P. In a particular embodiment adapted for use in a system of
25 am (8 to 10 in.) long, and 4
．． The inner pipe 62 has an outer diameter of 2.75 cm (1.1 in.) and a diameter of 0.47 J (0.19 in.).
) are provided with 40 uniformly spaced holes 68 having a diameter of . corrugated diagonally to the length and l
QcmXl5cm (4 in. x 6 in.)
A mesh insert 67 consisting of a piece of fine wire mesh made of stainless steel having a size of 1.5 mm is spirally wound tightly enough to be inserted into the pipe and expanded to completely fill the space. It should be appreciated that it is impossible to accurately depict such a tightly rolled spiral shape in the drawings. Approximately 10-1511. P. In another embodiment intended for a system of 5.25 c.
m (2.1 in.), and the internal pipe 62 has an outer diameter of 4.
．． It has an outer diameter of 0 cm (1.6 in.) and the hole 68 has a diameter of 0.6 cm (0.25 in.). In practice, the pressure drop in the device of the invention is sufficiently small, typically about Q. Q 7 kg/cj (l
psi), there is no appreciable efficiency loss, so any loss is more than compensated for by the significantly improved overall efficiency that is typically achieved.

The drop is small enough that it is difficult, if not impossible, to detect with the pressure needles used in standard refrigeration equipment.

Despite these long-standing problems, how to provide a turbulence generator and/or mixing device that sufficiently improves temperature sensing and control of TX valves and coil-type systems. No. 3, U.S. Pat.
No. 555,845, No. 3,740,967, and No. 4,222,949 have not been used as commercial equipment. Accordingly, the literature in the industry to the best of the applicant's knowledge suggests that the lengths of the circuit coils be made as equal as possible, that all circuit coils discharge into a common hexagonal pipe, and that the sensor sphere is connected to the discharge pipe from the hexagonal pipe. Clamping to the outside of the pipe is all that is possible, then the temperature is measured as accurately as possible and the fluid is considered to be mixed to the maximum extent achieved. ．． This misconception is believed to be the result of a lack of adequate awareness of the refrigerant fluid flow conditions in the evaporator coil and discharge pipe or manifold.

The refrigerant enters the coil as a low-volume liquid and evaporates into a high-volume vapor within its confined space, so that the vapor exit velocity is relatively high and the highly turbulent and/or Or, if no mixing method and corresponding device are provided, it includes all fluid flows, the flow in the coil is layered LA, the liquid particles are maintained in an entrained flow state without being mixed, and different coils There is little or no possibility that the flows from the As a result, before the temperature is detected by the sphere 50,
There is little chance that even a small amount of liquid refrigerant will evaporate. It is important that turbulence and mixing take place over the entire cross-section of the flow path, since any gaps allow the high-speed fluid in the corresponding section to pass through and maintain laminar flow conditions. , liquid particles are entrained,
This is because the purpose of the device is h4 damaged. In conventional devices, placing the sensor sphere 50 further along the suction pipe 56 does not make the situation much better, since the flow remains relatively laminar along the pipe. from the evaporator outlet, and from the TX
Adding the distance from the valve to the sphere introduces additional difficulties because the delay time for valve actuation increases. As evidence of the current lack of awareness of the problem, there is a traditional and well-debated debate about the best physical configuration of coils for equal loading; It has been considered important in the system to properly position the sensor sphere 50 on the periphery of the suction pipe in order to detect the superheat temperature as accurately as possible and to operate at a minimum degree of superheat. TX valve manufacturers emphasize the importance of proper positioning of the sensor sphere in their equipment manuals, but do not specify a specific location for this purpose.
There, it is preferred that the sphere is fixed in the horizontal part of the suction pipe, and in different positions depending on its diameter.
It is recommended that the clamps should be clamped at different positions on the periphery; It has been selected by
The results are often not good. The theoretically ideal position is the 6 o'clock position on the periphery of the horizontal suction pipe, where any small amount of liquid refrigerant passing through the pipe can be detected most accurately and therefore the least amount The degree of superheating can be allowed. In practice this is not a satisfactory position because there is lubricating oil in the refrigerant, which flows along the bottom of the pipe and thermally isolates the sensor sphere from the refrigerant fluid.

The normal position for this sphere is therefore the 4 o'clock or 8 o'clock position on the pipe periphery. It has been found that the position of the sensor sphere on the periphery of the device is of no importance if complete turbulence and mixing are provided, and should be as close to the valve as possible from an installation point of view, and It can be installed in the most convenient location for maintenance access. Also, the sensor need not be installed directly on the wall of the mixing device, which is the preferred location, but as close as possible to the outlet of the device. Furthermore, it has been shown that it is completely unnecessary to place the sensor sphere in the horizontal part of the suction pipe, and that the orientation of the device has no effect on its performance. It has also been shown that this device is relatively obtuse when installed with the inlet as the outlet, or vice versa, although this condition is of course not recommended. However, under such conditions, a slight decrease in operating efficiency is observed. The effectiveness of the device of this invention is readily apparent by visual inspection of the evaporator coil before and after its installation.
Before installation, the frost build-up on the different circuit coils is usually uneven, with some having frost all the way to the outlet, while others are frosted completely behind the outlet. frost does not form up to a distance of 100 m, indicating that the latter is starved of refrigerant and is operating at a capacity lower than its maximum cooling capacity. Furthermore, the common outlet member of the evaporator is only partially frosted. When the device is installed, all circuit coils, as well as the entire length of the suction manifold, will be frosted approximately equally, indicating that all circuit coils are now operating at full design capacity. Therefore, it is clear that it is possible to safely reduce the degree of superheating from the conventional level of approximately 5.5'C (10'F) to a low value of 2°C (4''F). Depending on the installation, the resulting cooling capacity improvement of the system can be between 25 and 35%.
It has been shown that previously the system was operating at only 74-80% of its possible capacity.

As a special example, 200 total 11. P. In an installation utilizing a compressor and eight forced air evaporator coils,
Before installing the device of this invention, the system had a room temperature of 13°C.
It took 3 hours and 10 minutes to cool from (55°F) to -2°F (-19°C). When installed, this device took 2 hours 10 minutes and improved efficiency by 29%, or compressor output by approximately 2 5 8 11.
P. It is thought that it was increased by . An important advantage of the use of this invention, along with its unexpected properties, is that it allows the size of the TX valve to be closely matched to the capacity of the evaporator coil without the valve losing control of refrigerant flow. This is the flexibility it provides in terms of installation without the need for adaptation. The capacity of a TX valve is determined by both the size of its flow opening and the head pressure across the opening, and in conventional installations it was important that this fit be as tight as possible. For example, a manufacturer may offer 21 different sizes of valves to cover the 0.5-180 ton range, but the 0.5-3 ton range may be configured in 0.5 ton increments. , followed by progressively increasing intervals up to a maximum value. If the valve is too large and high superheat values are utilized, the evaporator will be over- and under-supplied, resulting in reduced efficiency and, due to the large flow capacity of the valve when open, the liquid There is a danger that the air will reach the compressor. On the other hand, if the valve and coil sizes are closely matched, it will be necessary to maintain the head pressure above the minimum value because otherwise the flow capacity of the valve will be too small. This is a disadvantage for the system in winter when the air-cooled condenser is highly efficient and operates at low head pressures, which can be kept technically advanced by various techniques. This is necessary. This means that the power required to compress the refrigerant must also be kept at a correspondingly high and uneconomical value.

This loss of control is easily observed in practice. For example, if the evaporator fan stops for any reason, e.g. due to a ruptured fuse, or if the flow of the product to be cooled is interrupted, the coil load suddenly drops, more rapidly than can be controlled by the valve; The liquid will flood the compressor and become covered with frost. Liquid refrigerant washes away the lubricant and causes damage and damage to the valve. Additionally, if the automatic coil defrost system is not operating satisfactorily and the coils become covered with ice and the load on each coil drops and loses control, this will be easily detected by visual inspection of the coils. It is clear that

By installing one or more devices of the invention, this tight adaptation of the load capacity is no longer necessary and oversized valves can be utilized effectively. In a special example, i.e. in a system with a 1.5 ton evaporator, if the original 2 ton proportion valve is replaced by an 8 ton proportion valve, the 2
Adequate control was maintained with superheat values varying over a range of 100°F (°F). Therefore, in large orifice TX valves, in order to maintain a sufficiently high refrigerant flow rate through the valve, it is no longer necessary to technically maintain the head pressure at a high value, but to reduce it to an even lower value. This allows proper superheat control to be maintained at maximum evaporator capacity. This not only maximizes the efficiency of the system, but also offers the possibility of reducing the number of different sized valves required for the entire installation size range. As previously mentioned, the sensor sphere 50 is preferably mounted in the apparatus as close as possible to the apparatus outlet 54 where maximum mixing occurs. In the embodiment of FIG. 3, the outer tube 66 is provided with an elongated solid neck portion 66a. This neck portion 66a constitutes the outlet 54 and facilitates the fixation of the sphere to the device. In this embodiment, the interior of the internal pipe 62 is completely filled with metal wool 86 as a mixing medium instead of the rolled screen in the embodiment of FIG. FIG. 4 shows another arrangement in which the second turbulence/mixing device 4 of the invention
8. b, which has essentially the same structure as the first device 48, here designated by the reference numeral 48a, is connected in series with the first device, and the sensor sphere 50 is connected to the downstream device 48a. It is mounted on top. The second arrangement provides additional mixing and correspondingly improves the performance of the TX valve, by appropriately selecting the flow capacity of each internal passage and hole 68 along the suction line. It is possible to prevent the pressure drop from becoming so large. Mesh coil 67 (or metal wool body 86)
can be attached to one or both devices, and is shown attached to device 48a. FIG. 5 shows an embodiment in which the refrigerant flow path is provided by conduits forming two T-shaped connections 74 and 76, connected by U-shaped connections 78a and 78b, where the connections are Has a small internal cross-sectional diameter to increase flow velocity. The connecting portion 74 is connected to the common hender 42
splitting the refrigerant flow from the As it travels through connectors 78a and 78b at high speed, it is recombined into a single flow by collision of the leading end at the crossbar of connector 76. The collision of these two turbulent sub-flows results in even better mixing and therefore effective mixing before the refrigerant is delivered to the leg 77 of the second T-joint where the sphere 50 is attached. and turbulence occurs. Although in this embodiment the refrigerant flow is split into only two sub-streams, in other embodiments it may be split into three or more, all of which may be recombined simultaneously or sequentially.

FIG. 6 shows a configuration in which the device 72 is followed by the device 48, in which the effect of combining the two devices is obtained, and in this case the sphere 50 is attached to the downstream device 48. It will be done.

FIG. 7 shows another embodiment in which the apparatus is constituted by a vessel 80 having an inlet 82 for unturbulent, unmixed refrigerant and spaced apart from one another along the length of the vessel. 84 for turbulent and mixed refrigerant, both the inlet and the outlet being arranged radially with respect to the longitudinal axis of the vessel, thus controlling the fluid flow. The direction of the route is changing rapidly. The interior of the vessel is filled with a porous turbulent and mixing medium 86 through which all media must pass when moving from the inlet to the outlet. The movement of the refrigerant flow through numerous interconnected and chaotic channels in the medium 86 ensures the necessary complete turbulence and/or mixing. Suitable media include, for example, metal wool, foam or screens, or other suitable metal media, especially stainless steel or aluminium, which are sufficiently densely packed to provide a large pressure drop. The structure is configured to achieve the desired amount of turbulence and mixing without any turbulence. Other media can also be used, such as open cell porous plastics and ceramic foams. The sensor sphere 50 is placed as close to the outlet 84 as possible against the outer wall of the container, which has sufficient thermal conductivity.
The clamp is securely clamped at a position close to. By way of example, container 80 has a diameter of 10 cs+ (41 n.), a length of 25 cm (10 in.), and is filled with stainless steel wool. the wool body is surrounded by at least one layer of wire mesh;
It is preferable to prevent wool pieces from breaking and entering the system. FIG. 8 shows that the device 80 of FIG. 7 is utilized as a preturbulation and premixing device for the second downstream device 48.
Again, a configuration is shown in which the combined effects of the two devices are obtained.

FIG. 9 shows that the device consists of a straight pipe 66, the entire interior of which is filled with a tightly wound wire mesh 67, so that once again the entire refrigerant flow is impeded and sufficiently turbulent to the required extent. and an example in which they are mixed. In this embodiment, since there are no abrupt changes in the flow path except within the interstices of the wire mesh, this device is designed to provide a longer path than the turbulence and mixing devices previously described.
Preferably long, the sensor sphere 50 is mounted as close to the outlet end 54 as possible, as in the other embodiments. v! 4. Contains a tightly spirally wound stainless steel mesh. OeII (1.6in.
) using a vibrator 66 having an outer diameter of 10H. P.
As an example of the additional length required for the installed equipment in a system with a compressor of 480 mm, the pipe is
20 to 25 cm (8 to 1
0in. ) compared to the length of 4 5 cm (1 B
in. ) has a length of However, in another particular example, the device with a linear enclosure between the inlet and the outlet has a length of 251 (10 in.) and a length of 4 c.
It consists of a piece of pipe with an outside diameter of 1.6 in. Approximately 25caX 15cm (l Oi
n. x 6in. ) with the size of 6 dragons (0.2
5 in. ), a piece of permanent aluminum filter material formed from woven aluminum strands, such as those utilized as air conditioning filters, is rolled tightly into a cylinder and inserted into the pipe from the end. It will be inserted. This device has approximately 1011. P. The sensor sphere is fixed in the suction line immediately downstream of the device. Despite the relatively short length, the result is an increase in the cooling capacity of the coil by almost 20%.

[Brief explanation of drawings]

FIG. 1 is a schematic diagram of a typical refrigeration system including a first embodiment of the present invention, FIG. 2 is an enlarged vertical sectional view of the first embodiment of the device shown in FIG. 1, and FIG. 3 is a second embodiment of the system. A cross-sectional view similar to FIG. 2 showing the device, FIG. 4 is a vertical cross-sectional view of two devices arranged in series with the device of the first embodiment shown in FIG. 2, and FIG. 5 is a front view of the device of the fourth embodiment. 6 is a partial vertical sectional view of a device constructed by arranging the device of FIG. 2 and the device of FIG. 5 in series, FIG. 7 is a vertical sectional view of the device of the fifth embodiment, and FIG. A vertical sectional view of a device constructed by arranging the device in FIG. 2 and the device in FIG. 7 in series,
FIG. 9 is a longitudinal sectional view of the device of the sixth embodiment. 10... Refrigerant compressor, 12... Suction inlet, 14...
...High pressure outlet, 15...Conduit, l6...Am coil, l8...Inflow port, 20...Discharge port, 21...
Conduit, 22... Liquid accumulator, 24... Conduit, 26... Filter/dryer, 28... Liquid display device, 30... TX valve, 32... Distribution device, 3
4a. 34b...Circuit coil, 36a, 36b...
Inlet pipe, 38a, 38b... Inlet, 40a,
40b...Discharge port, 42...7 goo pipe to common,
44...Single discharge port, 46...Inflow port, 48...
Mixing device, 48a...Downstream device, 48b...Turbulent flow/mixing device, 50...Superheating temperature detection sphere, 51...
Clamp, 52...Capillary tube, 54...
Discharge port, 56... Conduit, 58.60... Fan, 6
2... Internal cylindrical pipe, 64... Other end, 66...
- External cylindrical pipe, 66a... Neck portion, 67... Spiral coil, 68... Hole, 70... Annular chamber, 72
... device, 74.76 ... T-shaped connection part, 77...
- Leg, 78a. 78b...U-shaped coupler, 80...
- Container, 82... Inlet, 84... Outlet, 86 Metal wool. F161 Patent Applicant Charles Gregory Agent Patent Attorney Pharmacist Minoru Agent Patent Attorney Yori
Kojiro Ta Representative Patent Attorney Masayuki TakagiFIG. 2 FIG. 9

Claims (25)

[Claims] (1) A method for detecting the temperature of refrigerant flowing out from the outlet of an evaporator coil of a refrigeration system and controlling a controllable evaporator valve that supplies liquid refrigerant to the inlet of the evaporator coil, the method comprising: In addition to supplying refrigerant to the interior of the turbulence generating and mixing device, said device is provided with a refrigerant flow passage and has a thermally conductive material on at least a portion of its wall, through which the internal temperature of the enclosure is controlled. turbulence and mixing generators, i.e., interrupting the total refrigerant flow and changing the direction of the total refrigerant flow to create turbulence and turbulence of all liquid and vapor refrigerant phases present in the refrigerant flow; generating turbulence and mixing of the refrigerant in the flow passage by means of said turbulence and mixing generating device which ensures mixing and ensures that only the mixed phase contacts the wall portion; and temperature sensing. A method for detecting refrigerant temperature and controlling refrigerant load, characterized in that the device detects the internal temperature of the enclosure at the wall portion and controls the evaporator valve according to the detected temperature. (2) The turbulence and mixing generating device receives the refrigerant in the first passage and delivers it to the second passage through the plurality of holes, and the flow passing through the holes causes the refrigerant to flow into the second passage. The impingement on the first side of the second passage causes an abrupt change in flow direction, causing a turbulent flow to be generated against the first side, and the temperature sensing device detects the second side of the second passage. 2. The method of claim 1, further comprising contacting the surface and being in heat exchange contact with the first surface through the second passageway wall. (3) The refrigerant is introduced into the first passage at one end, and the other end of the first passage is blocked, and the flow of refrigerant collides with the end, creating turbulent flow within the first passage. 3. A method according to claim 2, characterized in that the method is characterized in that: (4) The method according to claim 2 or 3, characterized in that the first passage is provided with a mixing device therein which prevents the flow of the refrigerant within the passage. (5) characterized in that the mixing device in the first passage is selected from metal wool, metal foam, metal screen, plastic foam or porous ceramic foam;
The method according to claim 4. (6) A turbulence and mixing generating device is formed from a conduit device that divides the refrigerant flow into two or more separate turbulent flows and regenerates the separate flows by subsequent collision with each other. Claim 1, characterized in that the two flows are coupled to generate turbulent flow between them, and the temperature detection device is disposed at the recombination point of the two flows.
Method described. (7) a turbulence and mixing generating conduit device for dividing the refrigerant into said two or more separate turbulent flows by impingement against a surface of the device transverse to the direction of flow of the refrigerant; 7. The method according to claim 6, characterized in that: (8) The turbulence and mixing generating device is characterized in that the chamber includes a porous mixed medium that prevents the total refrigerant flow and allows the refrigerant to pass between the inlet and the outlet. , the method of claim 1. (9) characterized in that the porous mixed medium is selected from metal wool, metal foam, metal screen, plastic foam or porous ceramic foam;
The method according to claim 8. (10) The inlet and the outlet to the enclosure are radial to the direction of flow of the refrigerant through the enclosure, and have a correspondingly abrupt change in the direction of flow. 9. The method according to 8 or 9. (11) Two turbulence and mixing generating devices are arranged in series with each other to increase turbulence and mixing of the refrigerant and improve temperature sensing.
10. The method according to any one of items 1 to 10. (12) Control of the refrigerant load on the evaporator coil of the refrigeration system is performed by a plurality of circuit coils connected in parallel with each other, and all of these circuits distribute the refrigerant through a flow control valve and refrigerant distribution controlled by a common thermostat. 12. A method according to claim 1, characterized in that the valves are connected via a device and the valves are controlled by a common superheat temperature sensor for controlling the refrigerant flow. . (13) A device for detecting the temperature of refrigerant flowing out of an evaporator coil outlet of a refrigeration system and controlling a controllable evaporator valve that supplies liquid refrigerant to an evaporator coil inlet, the device comprising: The enclosure has an inlet and an outlet for the refrigerant, has a refrigerant flow passage therein, has a thermally conductive material on at least a portion of its wall, and is configured to detect the internal temperature of the enclosure through the wall portion. A turbulence and mixing device is provided in the flow path to impede the total refrigerant flow and cause turbulence and mixing of the refrigerant due to changes in the direction of the total refrigerant flow to eliminate all liquid and vapor present therein. A turbulence and mixing generator to ensure turbulence and mixing of the refrigerant phase and contact of the mixed phase with the wall part, and a temperature sensing device to detect the internal temperature of the enclosure. is in heat conductive contact with the wall portion and a device adapted to control the evaporator valve in accordance with the sensed temperature. Device. (14) The turbulence and mixing generating device includes a device forming first and second passages having a common wall therebetween, the common wall having a plurality of holes through which the refrigerant flows. 1st
As the flow flows from the passageway to the second passageway, the holes cause turbulence and mixing of said flow to the second passageway by causing the flow to impinge on the first side of the second passageway, thereby abruptly changing the flow direction. 14. Device according to claim 13, characterized in that it is adapted to be generated within the passageway. (15) the first passageway is formed by a first tubular member, and the second passageway is formed by a second tubular member surrounding the first tubular member and forming an annular second passageway therebetween; 15. The apparatus of claim 14, wherein the holes are provided in the wall of the first tubular member and are adapted to direct coolant flow against the inner wall of the second tubular member. (16) One open end of the first tubular member constitutes an inlet to the first passage, and the other end of the member is closed so that the refrigerant flow impinges on the closed end, resulting in the flow of refrigerant into the first passage. characterized by generating turbulence in
16. Apparatus according to claim 15. (17) The first passage is filled with a porous mixed medium through which the refrigerant passes from the inlet to the plurality of holes. Apparatus described in section. 18. Device according to claim 17, characterized in that the porous mixing medium is selected from metal wool, metal foam, metal screen, plastic foam or porous ceramic foam. (19) A turbulence and mixing device includes a first coupling device that divides the refrigerant flow into two or more separate flows and subsequently combines the separate flows by impinging the flows against each other. a second connecting device that generates turbulent flow between the two, and a conduit device that connects the first and second connecting devices to cause separate flows between them; 14. Device according to claim 13, characterized in that it is arranged at the location of the coupling device. (20) the first coupling device directs the flow of refrigerant into two or more separate sections by impinging the flow of refrigerant against a surface of the coupling device disposed transversely to the direction of flow into the device; Claim 1 characterized in that the flow is divided into a flow of
9. The device according to 9. (21) The device according to claim 13, characterized in that the turbulence and mixing device comprises a porous mixing medium in the device, through which the refrigerant is passed from the inlet to the outlet. . 22. Device according to claim 21, characterized in that the porous mixing medium is selected from metal wool, metal foam, metal screen, plastic foam or porous ceramic foam. (23) characterized in that the inlet and outlet to the enclosure are radial to the direction of flow of the refrigerant through the enclosure and are adapted to produce a corresponding abrupt change in that direction; 23. The device according to claim 21 or 22. (24) Claim 1, characterized in that two turbulence and mixing devices are connected in series with each other to increase the turbulence and mixing of the refrigerant and improve temperature detection.
24. The device according to any one of items 3 to 23. (25) An evaporator coil consisting of a plurality of circuit coils, the circuit coils being interconnected in parallel so that all the coils are supplied with refrigerant for evaporation from a common control valve. an evaporator coil common member for receiving refrigerant from all of the circuit coils; and an evaporator coil common member operatively connected to a control valve for detecting and controlling the temperature of the refrigerant within the common member. 25. Device according to any one of claims 13 to 24, characterized in that it is used in a refrigeration system comprising a common superheat temperature sensor.