Method of calibrating overheating sensor

FIELD: physics.

SUBSTANCE: disclosed is a method of calibrating an overheating sensor (5) for a refrigeration system, according to which: the amount of liquid coolant in the evaporator (1) is increased, for example, by increasing the degree of opening of the control valve (3); at least one parameter, for example, temperature of the coolant coming out of the evaporator (1), is monitored, from which the overheating value of the coolant can be determined; the possibility of reducing said parameter is provided; when the value of the monitored parameter is set at an essentially constant level, the corresponding overheating (SH) value is taken as zero; the overheating sensor (5) is calibrated in accordance with said level at which the overheating value (SH) is equal to zero. A constant level of the value of said parameter indicates that the liquid coolant can pass through the evaporator (1) and, consequently, the overheating value of the coolant at the outlet of the evaporator (1) is equal to zero.

EFFECT: disclosed method enables to calibrate an overheating sensor at the operating site of the refrigeration system, owing to which there is no need to calibrate said sensor at the manufacturing plant and, as a result, the need to monitor conformity of calibration data of a particular sensor.

11 cl, 10 dwg

 

The technical FIELD

The present invention relates to a method of calibrating the sensor for overheating of the refrigeration system. The method is intended primarily for sensors installed in the refrigerant circuit of the refrigeration system, which also includes control valve, the evaporator and the compressor.

The LEVEL of TECHNOLOGY

The work of the refrigeration systems is typically controlled by varying the degree of opening of the regulating valve and/or opening and closing the regulating valve and, thus, the amount of liquid refrigerant entering the evaporator. It is desirable to control the regulating valve so that the entire entering the evaporator, the liquid refrigerant is completely evaporated to the exit of the evaporator, while it is also desirable that at the outlet of the evaporator or directly in front of the outlet pipe of the evaporator, the refrigerant present in the form of a mixture of liquid and gaseous phases. Such requirements due to the fact that in the case of withdrawal of refrigerant from the evaporator there is a possibility of its falling into the compressor, which may cause damage to the latter. On the other hand, if the liquid refrigerant evaporates completely, having passed only through the first part of the evaporator, the cooling capacity of the evaporator is not used in full.

How does the above state of the refrigerant, can be judged by the value the of it from overheating. Overheating is generally defined as the difference between the actual temperature of the liquid and the boiling point of this liquid. Overheating depends on the fluid temperature and its pressure. Therefore, the value of overheating is a suitable parameter for regulating the degree of opening of the regulating valve. In normal conditions it is desirable that the evaporator was observed a small, but clearly overheating. In this case, achieving the above-described state, i.e. the cooling capacity of the evaporator is used most effectively, while the risk of damage to the compressor due to entering of the liquid refrigerant from the evaporator to a minimum.

To operate a control valve to maintain the optimum values of overheating, it is necessary to provide the ability to accurately measure this value. This, in turn, is necessary to calibrate the sensor or sensors used to measure overheating or parameters that calculate the value of overheating. It is desirable that such a calibration was very accurate.

Known solutions, in accordance with which the calibration of the sensors overheating performed by individual calibration of each sensor on the factory that requires more labor and increases the cost of the sensors. It is extremely important that the calibration data were correlated with the sensor, to which they relate. For this calibration data can be written directly on the sensor, for example, connected with him printed circuit Board that is quite time-consuming and leads to an increase in the number of components of the sensor. In accordance with another variant of the calibration data may be stored separately, for example, on the corresponding controller. However, this method is fraught with considerable risk of errors caused by mismatch calibration data specific to the sensor.

In patent # US 5820262 disclosed sensor refrigerant, which is a single node that measure temperature and pressure, and calculates the value of overheating. The sensor includes a pressure transducer for measuring pressure of the refrigerant and the temperature Converter to measure its temperature. For measured values of temperature and pressure, the microprocessor calculates the value of superheat of the refrigerant. The sensor can be made with the possibility of self-calibration. The calibrator calibrates the values measured by the temperature sensors and pressure on the basis of the calibration data table temperature-pressure. In this calibration table shows the reference values of temperature and pressure, with which compare the corresponding measured values. To accomplish the above calibration tablecategories column values of pressure and column temperature values, moreover, these values are linked in mutual correlation.

DISCLOSURE of INVENTIONS

The present invention aims to provide a way to accurately calibrate the sensor overheating.

Another object of the invention is to provide a method of calibrating the sensor overheating when exercising which decreases the likelihood of errors in comparison with known methods.

Another object of the invention is to offer a less time-consuming compared to the known method of calibration of the sensor overheating.

An additional object of the invention is to provide a method of calibration of the sensor overheating, reduces the cost of manufacturing such a sensor.

To solve the above and other objectives of the present invention, a method for calibration of overheating sensor that is installed in the refrigeration system, containing control valve, the evaporator and the compressor, and the control valve, the evaporator, the overheating sensor and the compressor is hydraulically connected circuit through which flows the refrigerant.

This method includes the following steps:

- increase the share of liquid refrigerant in the evaporator,

- monitor at least one parameter by which to judge the value of superheat of the refrigerant,

- about the handle the containers can change this parameter to a

- when the value of the monitored parameter is set at essentially a constant level corresponding to the specified level is overheating taken for zero (SH=0),

- calibrate the sensor (5) overheating in accordance with the value of zero superheat (SH=0).

If necessary, calibration of the sensor overheating first, increase the share of liquid refrigerant in the evaporator. For this purpose, for example, increase the degree of opening of the control valve, reduce the rotation speed of the compressor or reduce the secondary flow medium through the evaporator. Below these steps are described in more detail.

With the increase in the share of liquid refrigerant in the evaporator, the boundary between liquid/mixed and gaseous refrigerant is shifted in the direction of the outlet pipe of the evaporator. As a consequence, the value of superheat of the refrigerant flowing from the evaporator decreases. Accordingly the value of the parameter, which is judged on the value of overheating.

Thus, when the boundary between liquid/mixed and gaseous refrigerant reaches the outlet of the evaporator, a small amount of liquid refrigerant flowing out of the evaporator, and pouring the evaporator has a zero overheating. If you continue to increase the share of liquid refrigerant amount flowing from the evaporator liquid cladogenetic will grow, but overheating will remain zero. Therefore, in this situation the value of the parameter, which is judged on the value of superheat is set essentially at a constant level.

That is, if you increase the proportion of liquid refrigerant in the evaporator and to monitor one or more parameters by which to judge the overheating, it will be observed the following. First, the specified parameter (or parameters) will change due to overheating, and then he reaches essentially constant level, since the value of superheat of the refrigerant is set to a constant zero level. This level can be used to calibrate the sensor overheating.

It is desirable to increase the share of liquid refrigerant so that it was sufficient for the liquid refrigerant hit the overheating sensor, mounted at the rear of the evaporator in the direction of flow, i.e. would have happened "Bay" of the sensor.

Because the evaporator short-term results, only a small amount of liquid refrigerant, the risk of damage to the compressor minimum,

The advantage of the proposed method is that it can be done, when the overheating sensor is installed in the cooling circuit. This allows you to calibrate at the place of installation of the refrigeration system and repeat it as necessary. Those who thus eliminating the need for calibration of the sensors at the factory, that avoids problems that arise when using the above known solutions. Thus, you no longer need to ensure that calibration data fit the sensors to which they relate, which eliminates one of the main sources of potential errors. In addition, freeing the manufacturer of the calibration, it is possible to reduce the cost of manufacturing sensors, because they are no longer required to provide the appropriate section in the production line.

Next, calibration of the inventive method can be performed as many times as needed, for example, under different conditions of temperature and/or pressure, or simply to compensate for the deviation of the sensor readings. Thus, it becomes possible to make relatively accurate calibration of the sensor.

Finally, taking as a reference point essentially constant zero overheating, you can calibrate the sensor with high precision.

The step of increasing the share of liquid refrigerant in the evaporator can be performed by increasing the degree of opening of the regulating valve. The control valve of the refrigeration system are usually installed to regulate the flow rate supplied to the evaporator of the refrigerant, i.e. with increasing degree of opening of the control valve increases the number is the primary objective in entering the evaporator of the refrigerant.

The degree of opening of the regulating valve can be increased gradually, i.e. smoothly, or, alternatively, sharply.

An alternative to increasing the share of liquid refrigerant in the evaporator can reduce the secondary flow medium through the evaporator. The evaporator of the refrigeration system operates as a heat exchanger, i.e. it is the exchange of heat between the flowing through him refrigerant and the secondary medium flowing through the evaporator, but not passing through the refrigerant circuit. Secondary medium can be liquid or gaseous, for example, in the form of a stream of air which is blown through the evaporator. In the latter case, for blowing air through the evaporator usually a fan. In this case, the secondary flow environment weaken the reduced speed of rotation of the fan, including the full stop.

The weakening of the flow of the secondary environment reduces the load on the refrigeration system, slowing down the evaporation of the refrigerant in the evaporator. As a result the share of liquid refrigerant increases.

Alternatively, to increase the share of liquid refrigerant in the evaporator is possible to reduce the rotation speed of the compressor. Decreasing the rotation speed of the compressor increases the pressure in the cooling circuit, which leads to an increase of the evaporation temperature of the refrigerant, resulting, in turn, decreases the temperature difference x is adgenta at the inlet and outlet of the evaporator. It slows down the evaporation of the refrigerant in the evaporator, resulting in an increase in the share of liquid refrigerant.

The step of tracking one or more parameters may include monitoring the temperature of the refrigerant at the evaporator outlet. With the increase in the evaporator the liquid fraction of the refrigerant, the refrigerant temperature at the exit when the pressure behaves as follows. Initially, it decreases as the boundary between the liquid/mixed refrigerant and the gaseous refrigerant is shifted in the direction of the outlet pipe. Thus, there is less time to heat the gaseous refrigerant after evaporation, which results in lowering the temperature. When the proportion of the liquid refrigerant increases so much that it begins to emerge from the evaporator, the temperature leaving the evaporator of the refrigerant is set at essentially a constant level corresponding to the evaporation temperature of the refrigerant when the refrigerant pressure. Thus, the achievement of the monitored temperature is essentially constant level serves as an indicator that the value of superheat of the refrigerant at the outlet of the evaporator has reached zero, which accordingly allows to calibrate the sensor.

Alternative or additionally, the step of tracking one or more parameters may predusmatriva the th measurement of the distance between the first and second walls of the overheating sensor, which depends on the pressure and temperature of the refrigerant at the evaporator outlet. In this embodiment, it is considered the overheating sensor that can directly measure the value of superheat of the refrigerant at the evaporator outlet. This can be, for example, a sensor with a flexible wall separating the cavity, which contains a fill fluid in thermal contact with the refrigerant from the refrigerant circuit. In this case, the pressure in the cavity depends on the temperature of the refrigerant, and the position of the flexible wall is determined by the ratio of pressure between the refrigeration circuit and the cavity. Thus, the position of the flexible wall can directly measure the value of superheat of the refrigerant. The flexible wall may, for example, be a membrane or a bellows.

The inventive method may also include the step of storing the results of phase calibration in the database. In this case, the phase calibration of the sensor overheating can be further carried out on the basis of data previously entered into the database. Calibration can be performed, for example, at different pressures, and the results be used for accurate calibration, covering a wide range of pressures.

Phase calibration of the sensor overheating may provide the solution of the linear equation, such as:

SH=a1UP +a2UT+b

where UPis a parameter representing the pressure of the refrigerant, UTis a parameter representing the temperature of the refrigerant, a1, a2and b are constant coefficients. In this case, the pressure and temperature of the refrigerant is measured separately. The coefficients a1and a2often known with some accuracy, whereas b is usually determined by the proposed method.

If the calibration of the claimed method was carried out, for example, at three different pressures, the equation SH=a1UP+a2UT+b can be solved as a system of three equations with three unknowns that will allow you to find all three constant coefficient and to improve the calibration accuracy of the sensor. However, in most cases, a satisfactory calibration accuracy can be obtained without it.

Alternatively, a linear equation may have the form:

SH=aU1+b

where U1is a parameter representing the value of superheat of the refrigerant at the evaporator outlet, a and b are constant coefficients. In this case, the monitored parameter is directly measured is overheating, which is measured directly, for example, as the distance between the two walls in the sensor of the above type.

Can also be used in other equations orders of magnitude, for example, square. Stage monitored the project for one or more parameters can be accomplished using the sensor overheating. Alternatively, these parameters can be measured using one or more additional sensors, such as temperature sensors.

BRIEF DESCRIPTION of DRAWINGS

Below the present invention is described with reference to the accompanying drawings, on which:

figure 1 schematically shows the evaporator of the refrigeration system operating under normal conditions;

on figa-2d shows an evaporator 1 during calibration;

figure 3-7 shows various examples of sensors overheating, allowing the calibration of the inventive method.

DETAILED description of the INVENTION

Figure 1 schematically shows the evaporator 1, is installed in the refrigerating system. The specified evaporator contains inlet pipe 2, is hydraulically connected to the regulating valve 3. The degree of opening of the valve 3 determines the amount of refrigerant supplied to the evaporator 1. The evaporator 1 has an outlet 4, hydraulically connected to the sensor 5 overheating.

The sensor 5 overheating measures the value of one or more parameter by which to judge the value of superheat of the refrigerant leaving the evaporator 1 through the outlet 4. It can measure the corresponding values of temperature and pressure of the refrigerant at the outlet of the evaporator 1. Alternative sensor can measure the value of a single R is a representative parameter, on the basis of which we can estimate the value of superheat of the refrigerant at the outlet of the evaporator.

The sensor 5 overheating transmits the measurement results to the control device 6. On the basis of these results, the control unit 6 generates a control signal for the regulating valve 3, by adjusting the degree of opening in accordance with the value of overheating, thus, to maintain a small, but clearly overheating that achieves the optimal conditions of operation of the refrigeration system. Control unit 6 may calculate the value of superheat of the refrigerant at the outlet of the evaporator 1 according to the data measured by the sensor 5 overheating, and, consequently, to adjust the degree of opening of the regulating valve 3 based on the results of the calculations. Alternatively, the controller 6 may control the regulating valve directly on the data measured by the sensor 5,

Figure 1 shows that in the evaporator 1 has a refrigerant in liquid and in gaseous state. The input pipe 2 mostly liquid refrigerant, and at the outlet of the 4 - predominantly gaseous. At intermediate points the refrigerant is in the form of a mixture of liquid and gaseous phases.

The graph in figure 1 shows the dependence of superheat of the refrigerant from the traversed path through the evaporator 1. Of g is the Afik well seen, while the refrigerant is in a liquid state or in a state of a mixture of liquid and gaseous phases, overheating essentially equal to zero. However, as soon as the refrigerant goes completely in the gaseous state, is overheating begins to increase.

On figa-2d shows the evaporator 1 with 1 during calibration. In the case shown in figa, in the evaporator 1 is predominant gaseous phase, i.e. the efficiency of the refrigeration system is not great. The graph on figa shows the dependence of superheat of the refrigerant at the outlet of the evaporator 1 from the time during sensor calibration 5 overheating. It can be seen that the value of overheating in this case is relatively large.

In the case shown in fig.2b, the share of liquid refrigerant in the evaporator 1 has increased, for example, by increasing the degree of opening of the regulating valve 3. In the drawing it is seen that the line marking the boundary between the two-phase mixture and pure gaseous refrigerant is shifted in the direction of the outlet pipe 4. However, a relatively large portion of the evaporator 1 still contains the evaporator in the gas phase. The graph shows that the value of superheat of the refrigerant at the outlet of the evaporator 1 has decreased compared with the value observed in the case shown in figa, but still relatively high.

In the case shown in figs, the share of liquid refrigerant in ispai is barely 1 increased even more. In the drawing it is seen that the line marking the boundary between the two-phase mixture and pure gaseous refrigerant, ends at the location of the outlet pipe 4, i.e. the refrigeration system is operating optimally. The graph shows that the value of superheat of the refrigerant at the outlet of the evaporator 1 has reached a zero level. You can also see that the time derivative curve from overheating is at this point the gap. This gap can be registered, having, thus, a clear indication that achieved optimal working conditions. The drawing also shows that a small amount of liquid spilled out of the evaporator 1 and numb in the sensor 5 overheating.

In the case shown in fig.2d, the share of liquid refrigerant in the evaporator 1 has increased even more, resulting in an even greater amount of liquid refrigerant is released from the evaporator 1 and numb in the sensor 5 overheating. That is, there was a "Bay" of the sensor 5 with the liquid refrigerant. The graph shows that the value of superheat of the refrigerant at the outlet of the evaporator 1 is essentially constant zero level. Therefore, the value of overheating, as measured by the sensor 5, can be taken as zero and thus to calibrate the sensor. Upon completion of calibration, the share of liquid refrigerant in the evaporator 1 can be reduced and return the system to normal operating conditions.

Figure 3 until the EN of the first exemplary embodiment of the sensor 5 overheating for use in the refrigeration system. The sensor 5 includes a bellows 7, covering the inner cavity 8, containing fill fluid 9. It is desirable that thermostatic characteristics of the isolating liquid 9 was similar to the refrigerant circulating in the refrigeration circuit of the system, and ideally would be identical to that refrigerant.

The sensor 5 overheating installed in the cooling circuit; the flow of the refrigerant is indicated by arrows 10.

Since the bellows 7 has a thermal conductivity, the temperature of the filling liquid 9 is responsive to the temperature of the refrigerant. And since the inner cavity 8 is essentially closed, the pressure depends on the temperature.

The bellows 7 expands and shrinks in accordance with the pressure change in the inner cavity 8 and the refrigeration circuit. Accordingly, the position of the first wall 11 is determined by the ratio of these two pressures, i.e. it is defined as the temperature and pressure of the refrigerant. Therefore, the position of the first wall 11 can measure the value of superheat of the refrigerant. The first wall 11 is placed a permanent magnet 12 and the second wall 14 has a sensor 13 Hall. The position of the first wall 11 defines the distance between the first and second walls 11, 14, which can be measured by the sensor 13 Hall due to the presence of the first wall 11 of the permanent magnet 12. Thus, the sensor 5 shown in Fig., can measure directly the value of superheat of the refrigerant.

Figure 4 shows a second exemplary embodiment of the sensor 5 for overheating of the refrigeration system. Like the sensor 5 overheating, shown in figure 3, the sensor 5 overheating, shown in figure 4, contains the bellows 7, the permanent magnet 12 and the sensor 13 Hall. However, the sensor 5 overheating, shown in figure 4, provided with a compression spring 15 mounted in the cavity 8 of the sensor 5. The compression spring 15 moves the first wall 11 in the direction from the second wall 14. In the case of the sensor 5 overheating, shown in figure 4, there is no need to fill the inner cavity fills with fluid, although it is not excluded. To measure the temperature of the refrigerant at the second wall 14 includes a probe 16. Thus, the refrigerant pressure can be measured by the distance between the first wall 11 and the second wall 14 by means of a permanent magnet 12 and the sensor 13 Hall, and its temperature by sensor 16. These two measured values, you can calculate the value of overheating.

Figure 5 shows a third exemplary embodiment of the sensor 5 for overheating of the refrigeration system. The sensor 5 includes a membrane 17, mounted in the housing 18 in such a way that it separates the cavity 8 is filled with the filling liquid 9 from the refrigerant in the refrigeration circuit. The membrane 17 conductive, therefore, the temperature is filled with the soup liquid 9 is responsive to the temperature of the refrigerant in the circuit. As in the case described with reference to figure 3, the pressure in the inner cavity 8 is determined by the temperature of the refrigerant. The position of the membrane 17 is determined by the ratio of the pressure of the refrigerant in the refrigeration circuit and the cavity 8, i.e. it is defined as the temperature and pressure of the refrigerant, and therefore, the position of the membrane 17 can measure the value of superheat of the refrigerant.

On the membrane 17 has a permanent magnet 12, and opposite it on the wall of the housing 18 includes a probe 13 Hall. Thus, by means of the sensor 13 of the Lobby, you can measure the distance between the membrane 17 and the wall on which it is mounted, and thus, is overheating.

Figure 6 shows the fourth embodiment of the sensor 5 for overheating of the refrigeration system. The sensor 5 includes a silicon chip 19 mounted in the cooling circuit. In the Central part of the silicon chip 19 is installed membrane 20 so as to form a cavity 21 in which is maintained essentially constant pressure is usually very low or essentially a vacuum. The membrane 20 is bent under the action of the pressure in the cavity 21 and the refrigeration circuit. Since the pressure in the cavity 21 is essentially constant, the degree of deflection of the membrane 20 can measure the pressure in the cooling circuit.

The membrane 20 has a load cell (not until the Han) to measure the deflection of the membrane. It is connected to the measuring device by means of electrodes 22. To obtain data on the temperature of the refrigerant of the load cell is equipped with a bridge circuit (not shown) of the four resistors embedded in the surface of a silicon chip 19 in place of the membrane 20. The resistors are designed so that with increasing pressure the resistance of two of the four resistors is growing, while the other two - drops with increasing temperature the resistance of all four resistors rises (or falls). This allows you to calculate or at least estimate how the temperature and pressure of the refrigerant on the readings of the load cell, and, thus, to calculate the value of overheating.

7 shows a fifth exemplary embodiment of the sensor 5 for overheating of the refrigeration system. Sensor design 5 overheating, shown in Fig.7, a similar sensor design shown in Fig.6. However, in this case, the cavity 21 includes filling the liquid 9. Filling the fluid 9 is supplied from the reservoir 23 through the capillary tube 24.

Filling the liquid 9 is thermally connected to the refrigerant of the refrigerant circuit through the membrane 20, so its temperature changes with the temperature of the refrigerant. As a result, the pressure in the cavity 21 is defined by this temperature, just as it was described in the case illustrated in figure 5. Rela is estwenno according to the degree of deflection of the membrane, measured by the load cell, it is possible to directly measure the value of superheat of the refrigerant.

1. A method of calibrating the sensor (5) overheating installed in the refrigeration system, containing control valve (3), the evaporator (1) and the compressor, and the control valve (3), the evaporator (1), sensor (5) overheating and the compressor are hydraulically linked, forming a circuit through which flows the refrigerant, and in accordance with the specified method:
- increase the share of liquid refrigerant in the evaporator (1),
- monitor at least one parameter by which to judge the value of superheat of the refrigerant,
- provide the possibility of changing the value of the specified parameter,
- when the value of the monitored parameter is set at essentially a constant level corresponding to the specified level value (SH) overheating taken for zero (SH=0),
- calibrate the sensor (5) overheating in accordance with the value of zero (SH) superheat (SH=0).

2. The method according to claim 1, wherein the step of increasing the share of liquid refrigerant in the evaporator (1) increase the degree of opening of the regulating valve (3).

3. The method according to claim 2, in which the degree of opening of the regulating valve (3) increase gradually.

4. The method according to claim 1, wherein the step of increasing the share of liquid refrigerant in the evaporator (1) to reduce the flow of secondary fluid che is ez evaporator (1).

5. The method according to claim 1, wherein the step of increasing the share of liquid refrigerant in the evaporator (1) reduce the rotation speed of the compressor.

6. The method according to any one of claims 1 to 5, in which the step of monitoring at least one parameter monitor the temperature of the refrigerant at the evaporator outlet (1).

7. The method according to any one of claims 1 to 5, in which the step of monitoring at least one parameter monitor the distance between the first and second walls of the sensor (5) overheating, dependent on both pressure and temperature of the refrigerant at the outlet of the evaporator (1).

8. The method according to any one of claims 1 to 5, further comprising the step of storing the results obtained in the calibration step in the database.

9. The method according to claim 8, in which the calibration of the sensor (5) overheating produce in the future on the basis of data previously stored in the database.

10. The method according to any one of claims 1 to 5, 9 in which at the stage of calibration of the sensor (5) overheating solve the linear equation.

11. The method according to any one of claims 1 to 5, 9 in which the tracking of at least one parameter is performed by a sensor (5) overheating.



 

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Refrigerator // 2409794

FIELD: heating.

SUBSTANCE: refrigerator has assembly compartment, compressor arranged in assembly compartment, and cooling fan of assemblies for air cooling assemblies, which is located in assembly compartment, ambient temperature sensor having the possibility of ambient temperature measurement around the refrigerator, failure monitor having the possibility of detecting emergency stop of cooling fan of assemblies, controller having the possibility to stop the compressor if failure monitor detects emergency stop of cooling fan of assemblies and if ambient temperature measured with ambient temperature sensor is higher than the specified value and display device having the possibility of displaying the failure of the cooling fan assemblies when the controller stops the compressor.

EFFECT: refrigerator is capable of preventing excess temperature increase of assembly compartment in which assembly cooling fan is installed, and temperature of outer housing of refrigerator of cooling fan of assemblies is stopped in case of fault.

17 cl, 11 dwg

FIELD: machine building.

SUBSTANCE: cooling or heating system contains at least compressor (2), condenser (4), adjusting device (17A), evaporator (20) and control device (7A). Control device (7A) receives liquid from condenser (4) and has an outlet orifice into pipeline (9) for condensate and inlet facilities coming into signal channel (6, 10). Pipeline (9) for condensate is coupled with adjusting device (17A). Control facilities (12, 13) are connected to the signal channel for control over adjusting device (17A) opening. The system is equipped with evaporating facilities (8, 11, 18, 34) for evaporation of liquid coming into signal channel (6, 10). Control device (7A) is installed in the condenser or near inlet orifice of condenser (4), owing to which the said control is actuated with amount of liquid evaporated in signal channel (6, 10).

EFFECT: reduced losses of power.

17 cl, 7 dwg

FIELD: power industry.

SUBSTANCE: thermal-pipe steam-ejector cooling machine includes evaporation chamber of high pressure, which is connected to nozzle inlet of ejector. Receiving chamber of ejector is connected to evaporation chamber of low pressure. Diffuser is connected to condensation chamber equipped with wick. Evaporation chambers of high and low pressure are placed coaxially in one housing, their side walls are covered from the inside with wicks covered in their turn with casings with gaps at upper and lower edge walls. Evaporation chambers are divided between each other as to steam with horizontal partition connected to casing of evaporation chamber of high pressure. Inside evaporation chamber of high pressure there located is entrainment trap and receiving pipeline connected to distributing pipeline located in evaporation chamber of low pressure. After horizontal partition, the housing is equipped on the lateral side with vertical partitions after which there placed are condensing chambers covered from the inside with their wicks separated between each other with a partition into high-pressure segment and low-pressure segment. Ejectors are mounted into vertical partitions of condensing chambers and connected with their nozzle inlets to evaporation chamber of high pressure through distributing and receiving pipelines.

EFFECT: increasing efficiency of thermal-pipe steam-ejector cooling machine.

5 dwg

FIELD: heating.

SUBSTANCE: cooling circuit for circulation of carbon dioxide as cooling agent in it has the first expansion device for expansion of cooling agent from high pressure to intermediate pressure and the second expansion device for expansion of cooling agent from intermediate pressure to evaporation pressure. The first expansion device is made in the form at least of two in-parallel connected valves (a, b, c, d) so that in case of failure in the valve (a) or at the valve (a) the latter is switched off, and at least one of the remaining operating valves (b, c, d) continues providing the controlled operation of cooling circuit.

EFFECT: use of invention excludes the need for switching off the whole cooling circuit in case of failed valve.

13 cl, 1 dwg

FIELD: heating systems.

SUBSTANCE: suction orifice tube intended for refrigerating device includes suction tube (13) routed parallel to suction tube (13), orifice tube (14) and adhesive tape (19), the middle strip (20) of which is bonded to orifice tube (14), and two side strips (21, 22) enveloping middle strip (20) are bonded to suction tube (13) and covered on suction tube (13) from the side opposite to orifice tube (14). Free end of side strip (21, 22) is sealed with plastic or elastic mixture. Suction orifice tube manufacturing device has at least the first and the second roller (1, 2; 3, 4; 5, 6; 7, 8), the circles of which face each other and form clearance (15, 24); at that, at least on circumferential surface of the first roller (1; 3; 5; 7) there is slot (10, 25) for suction tube for directing suction tube (13) through clearance (24), and at slot bottom (10, 25) for suction tube there formed is slot (12) for orifice tube for directing orifice tube (14) in contact with suction tube (13).

EFFECT: use of invention will allow increasing resistance of suction orifice tube.

9 cl, 8 dwg

FIELD: heating.

SUBSTANCE: proposed invention relates to a refrigerating unit with a throttle pipe (1) and a suction pipe (2) for cooling agent; the throttle pipe (1) in the first point (A) of the suction pipe (2) is inserted into the suction pipe (2) and connected to it. The throttle pipe (1) and the suction pipe (2) are interconnected in another, second point (B) of the suction pipe (2) where the outer surfaces of the throttle pipe (1) and the suction pipe (2) are contacting. As per the invention the outer surfaces of the throttle pipe (1) and the suction coil (2) in the second point (B) are interconnected by ultrasonic welding. The proposed invention relates also to the method of connection of the throttle pipe (1) and the suction pipe (2).

EFFECT: application of the invention allows for the cheap and simple protection of the throttle pipe against crumpling at the point of insertion into the suction pipe.

6 cl, 1 dwg

FIELD: mechanics.

SUBSTANCE: cooling loop (2) for circulation of coolant in preliminary specified direction of flow contains in the direction of flow heat-eliminating heat exchanger (4), throttle valve (8) of evaporator, evaporator (10), compressor (22), internal heat exchanger (16), "cold face" of which is located between evaporator (10) and compressor (22), sensor (24) of temperature on inlet, located between evaporator (10) and internal heat exchanger (16), and sensor (26) of temperature on inlet, located between internal heat exchanger (16) and compressor (22), and control device (28) for control of throttle valve (8) of evaporator on the basis of measurements by temperature sensors on outlet and inlet. Control device is implemented with ability of control by throttle valve (8) of evaporator on the basis of installation of temperature on outlet in sensor (24) of temperature on inlet and shift of temperature installation on outlet on the basis of measurement by sensor (26) of temperature on outlet.

EFFECT: providing of adaptation of cooling loop to different conditions of operation in winter and summer modes.

12 cl, 1 dwg

Refrigerating unit // 2362095

FIELD: instrument making.

SUBSTANCE: invention relates to refrigerating equipment. The proposed refrigerating unit incorporates consecutively mounted device to increase operating medium temperature and pressure, condenser, throttling device and evaporator. It comprises additional pipeline with its input connected to aforesaid device that serves to increase operating medium temperature and pressure and output connected to condenser output and throttling device input. Aforesaid additional pipeline is fitted parallel to the said condenser and furnished with superheated vapor metered-feed device that receives the said superheated vapor from the device to increase operating medium temperature and pressure. The superheated vapor metered-feed device represents a jet, electromagnetic valve, or servo-drive gate.

EFFECT: increased refrigeration ratio.

2 cl, 4 dwg

FIELD: heating; refrigerating or freezing plants.

SUBSTANCE: closed refrigerating circuit comprises compressor (1), condenser (2), evaporator (4), receiver (9), capillary tube (8) between condenser and receiver, capillary tube (10) between receiver and evaporator and thermal contact (11) between suction pipeline and receiver. Suction pipeline is oriented so that sucked gas passes through receiver from its lower part to upper part. Cooling agent in receiver flows from its upper part to lower part. There is thermal contact (12) between suction pipeline and capillary tube (8), which connects condenser and receiver.

EFFECT: superheating of sucked gas, prevention of water condensation in suction pipeline and increased efficiency factor.

2 cl, 3 dwg

FIELD: cooling equipment, particularly to control coolant flow.

SUBSTANCE: flow regulator is formed of capillary tubes serially connected one to another and having different inner diameters and lengths. The capillary tubes are arranged so that capillary tube having greater diameter is installed before one having lesser diameter in direction of coolant flow from cooling unit condenser.

EFFECT: increased efficiency of cooling unit operation in cooling and heat pump regimes, as well as simplified manufacturing and computation.

2 dwg

FIELD: cooling equipment, particularly to control coolant flow.

SUBSTANCE: flow regulator is formed of capillary tubes serially connected one to another and having different inner diameters and lengths. The capillary tubes are arranged so that capillary tube having greater diameter is installed before one having lesser diameter in direction of coolant flow from cooling unit condenser.

EFFECT: increased efficiency of cooling unit operation in cooling and heat pump regimes, as well as simplified manufacturing and computation.

2 dwg

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