KR101317541B1 - Two-stage compression refrigerating device - Google Patents

Abstract

An object of the present invention is to provide a refrigeration apparatus that can maintain high efficiency even when the refrigerant suction pressure is low.
In the two stage compressed refrigeration unit (1), the first stage oil separator (8) is installed between the first stage compressor (2) and the second stage compressor (3) to supply oil to the first stage compressor (2). To reflux, install a second stage oil separator (9) on the discharge side of the second stage compressor (3) to reflux the oil in the second stage compressor (3), and rotate the first stage compressor (2) according to the refrigeration load. The number is controlled, the theoretical intermediate pressure Pmth is calculated from the square root of the product of the suction pressure Ps and the discharge pressure Pd, and the difference between the theoretical intermediate pressure Pmth and the suction pressure Ps is a predetermined lower limit differential pressure. When larger than (ΔPmin), the rotation speed of the second stage compressor 3 is controlled so that the intermediate pressure Pm matches the theoretical intermediate pressure Pmth, and the theoretical intermediate pressure Pmth and the suction pressure Ps are controlled. When the difference of) is less than or equal to the lower limit differential pressure ΔPmin, the second pressure of the compressor 3 is adjusted so that the intermediate pressure Pm matches the suction pressure Ps plus the lower limit differential pressure ΔPmin. Can controls.

Description

Two Stage Compression Refrigeration Unit {TWO-STAGE COMPRESSION REFRIGERATING DEVICE}

The present invention relates to a two stage compression refrigeration apparatus.

For a refrigeration apparatus, it is desired to realize a high coefficient of performance (COP) and to cope with a wide range of evaporation temperatures of the refrigerant in the evaporator. In order to achieve a high coefficient of performance in the two-stage compression refrigeration apparatus, it is necessary to optimize the load sharing between the compressor of the first stage and the compressor of the second stage.

For example, Patent Document 1 describes an intermediate pressure Pm which is the discharge pressure of the first stage compressor (the suction pressure of the second stage compressor), and the suction pressure Ps of the first stage compressor and the discharge pressure of the second stage compressor. The technique which prevents the fall of the efficiency of a refrigeration apparatus by changing the stroke volume of a compressor so that it may correspond to the square root (√) Ps of the product of (Pd) is described.

As a compressor for a refrigerating device, a type of supplying oil for cooling and lubrication and providing an oil separator on the discharge side is widely used. Usually, in a two stage compression refrigeration apparatus, an oil separator is arranged in the discharge flow path of the 2nd stage compression apparatus, and the oil isolate | separated by the discharge pressure is refluxed by the 1st stage and the 2nd stage compressor.

Japanese Patent Application Publication No. 2007-138919

In the conventional two-stage compression refrigeration apparatus, when the difference between the suction pressure Ps and the discharge pressure Pd becomes large, the refrigerant dissolved in the oil introduced into the low pressure space of the first stage compressor flashes (momentarily) due to the pressure difference. Evaporation) increases. This causes a problem that the amount of refrigerant that can be sucked by the compressor through the evaporator is reduced and the efficiency of the refrigeration apparatus is lowered.

In view of the above problems, an object of the present invention is to provide a refrigeration apparatus that can maintain high efficiency even when a refrigerant suction pressure is low.

In order to solve the above problems, the refrigerating device according to the present invention, the first stage compressor capable of controlling the rotational speed, the first stage oil separator, the second stage compressor independent of the first stage compressor in the refrigerant circulation flow path And a first stage oil flow path provided through a second stage oil separator, a condenser, an expansion valve, and an evaporator, for returning the oil separated by the first stage oil separator to the first stage compressor, and the second stage. A second stage oil passage for returning the oil separated by the oil separator to the second stage compressor, suction pressure detecting means for detecting the suction pressure of the first stage compressor, and a discharge pressure of the first stage compressor. Intermediate pressure detecting means, discharge pressure detecting means for detecting the discharge pressure of the second stage compressor, first stage control means for controlling the rotational speed of the first stage compressor in accordance with a refrigeration load, The theoretical intermediate pressure is calculated from the square root of the product of the detected value of the air suction pressure detecting means and the detected value of the discharge pressure detecting means, and the difference between the theoretical intermediate pressure and the detected value of the suction pressure detecting means is less than the predetermined lower limit differential pressure. If large, the rotation speed of the second stage compressor is controlled to match the detected value of the intermediate pressure detecting means with the theoretical intermediate pressure, and the difference between the theoretical intermediate pressure and the detected value of the suction pressure detecting means is 2nd which controls the rotation speed of a said 2nd stage compressor so that the detection value of the said intermediate pressure detection means may match the detection value of the said suction pressure detection means to the value which added the said lower limit differential pressure, when it is below the said lower limit differential pressure. However, it is assumed to have a control means.

In addition, the refrigerating device of the present invention is provided with evaporation temperature detecting means for detecting the evaporation temperature of the evaporator, the first stage control means, the rotation speed of the first stage compressor in accordance with the detection value of the evaporation temperature detection means May be controlled.

In the refrigerating device of the present invention, the first stage compressor and the second stage compressor may each be a screw compressor.

According to the present invention, since oil separators are provided on the discharge side of the compressors in each stage, oil at its discharge pressure is supplied to each compressor. As a result, the supply pressure of the oil is not excessively increased, and the refrigerant dissolved in the oil is not flashed to substantially reduce the capacity of the compressor (in particular, the refrigerant that can be sucked by the first stage compressor through the evaporator can be sucked in). The amount never decreases). In addition, since the second stage control means maintains the difference between the actual intermediate pressure and the suction pressure more than a certain value even when the theoretical intermediate pressure decreases, it is possible to secure the pressure difference required to supply oil to the first stage compressor. Therefore, trouble due to oil breakage can be prevented.

BRIEF DESCRIPTION OF THE DRAWINGS The block diagram of the refrigeration apparatus of one Embodiment of this invention.
FIG. 2 is a diagram illustrating a relationship between an evaporation temperature and a refrigerant pressure at each location in the refrigerating device of FIG. 1. FIG.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings. The structure of the refrigeration apparatus 1 which is one Embodiment of this invention is shown in FIG.

The refrigerating device 1 is provided through a first stage compressor 2, a second stage compressor 3, a condenser 4, an expansion valve 5, and an evaporator 6, and a refrigerant circulation in which a refrigerant is enclosed. It has a flow path 7. The 1st stage compressor 2 and the 2nd stage compressor 3 are the oil-cooled-type screw compressors of the inverter drive which can respectively independently control the rotation speed.

The refrigerating device 1 is a first to separate the cooling oil from the refrigerant discharged by the first stage compressor 2 in the refrigerant circulation flow path 7 between the first stage compressor 2 and the second stage compressor 3. A stage oil separator (8) is further provided to separate cooling oil from the refrigerant discharged by the second stage compressor (3) in the refrigerant circulation flow path (7) between the second stage compressor (3) and the condenser (4). The second stage oil separator 9 is provided. The refrigeration apparatus 1 includes a first stage oil passage 10 for refluxing the cooling oil separated by the first stage oil separator 8 to the suction and low pressure portions of the first stage compressor 2, and the second stage. A second stage oil passage 11 for refluxing the cooling oil separated by the oil separator 9 to the suction and low pressure portions of the second stage compressor 3 is further provided.

In addition, the refrigerating device 1 includes a suction pressure detector 12 that detects the suction pressure Ps of the first stage compressor 2, and a refrigerant between the first stage compressor 2 and the second stage compressor 3. An intermediate pressure detector 13 which detects the pressure of the circulation passage 7, that is, the discharge pressure of the first stage compressor 2 and the suction pressure of the second stage compressor 3; However, the discharge pressure detector 14 which detects the discharge pressure Pd of the compressor 3 and the evaporation temperature detector 15 which detects the evaporation temperature Te of the refrigerant | coolant in the evaporator 6 are provided.

In the refrigerating device 1, cooling oil is supplied to the first stage compressor 2 from the first stage oil separator 10 by the differential pressure between the intermediate pressure Pm and the suction pressure Ps, and the second stage compressor ( 3) Cooling oil is supplied from the 2nd stage oil separator 11 by the differential pressure of discharge pressure Pd and the intermediate pressure Pm.

In addition, the refrigerating device 1 includes a first stage control device 16 for controlling the rotation speed of the first stage compressor 2 and a suction pressure detector based on the detected value Te of the evaporation temperature detector 15. 12) the control device 17 which controls the rotation speed of the 2nd stage compressor 3 based on the detection value Ps, Pm, Pd of the intermediate | middle pressure detector 13 and the discharge pressure detector 14 is provided. . The control device 16 and the control device 17 may be independent programs or control routines realized by a single computer.

The first stage control device 16 controls the rotation speed of the first stage compressor 2, for example, to maintain the refrigeration load, that is, the detected value Te of the evaporation temperature detector 15 at the set temperature Ts. Adjust by well-known PID control.

The second stage control device 17 determines the target value Pms of the intermediate pressure Pm based on the detection values of the suction pressure detector 12 and the discharge pressure detector 14, and targets the intermediate pressure Pm. In order to match the value Pms, the rotation speed of the second stage compressor 2 is controlled by known PID control or the like.

This target value Pms is determined as follows. First, the second stage control device 17 is a theoretical intermediate pressure (S) which is the square root of the product of the suction pressure Ps detected by the suction pressure detector 12 and the discharge pressure Pd detected by the discharge pressure detector 14. Pmth) = {√ (Ps · Pd)}. Then, the second stage control device 17 obtains the difference ΔP between the theoretical intermediate pressure Pmth and the suction pressure Ps, and compares it with the preset lower limit differential pressure ΔPmin. When the differential pressure ΔP is greater than the lower limit differential pressure ΔPmin, the second stage control device 17 sets the target value Pms to the theoretical intermediate pressure Pmth, and the differential pressure ΔP is the lower limit differential pressure ΔPmin. If it is below, the target value Pms is set to the value (Ps + (DELTA) Pmin) which added the lower limit differential pressure (DELTA) Pmin to the suction pressure Ps which the suction pressure detector 12 detected.

Lower limit differential pressure (DELTA) Pmin is a pressure required in order to ensure the flow volume of the cooling oil required for the 1st stage compressor 2, and is determined by the piping resistance of the 1st stage oil flow path 10. As shown in FIG. This lower limit differential pressure (DELTA) Pmin is a fixed value (for example, 0.2 Mpa) which multiplied the safety factor and the value determined in the rated operation conditions of the 1st stage compressor 2 normally, It is good also as a value changed according to rotation speed.

2 shows the relationship between the suction pressure Ps, the intermediate pressure Pm, and the discharge pressure Pd. The suction pressure Ps is determined by the evaporation temperature of the refrigerant in the evaporator 6. The discharge pressure Pd is determined by the condensation temperature of the refrigerant in the condenser 4. If the temperature of the cooling water supplied to the condenser 4 is constant and the capacity of the condenser is sufficiently large, the condensation temperature becomes substantially constant. Therefore, in this embodiment, the discharge pressure Pd may be considered to be substantially constant.

As shown, when the evaporation temperature of the refrigerant in the evaporator 6 is lower than −50 ° C., the differential pressure ΔP between the theoretical intermediate pressure Pmth and the suction pressure Ps is the lower limit differential pressure ΔPmin (0.2). MPa) or less. At this time, the second stage control device 17 sets the target value Pms of the intermediate pressure Pm to a pressure Ps + ΔPmin that is higher by the lower limit pressure ΔPmin than the suction pressure Ps. This makes it possible to sufficiently supply the cooling oil to the first stage compressor 2, thereby preventing trouble of the first stage compressor 2. At the same time, an excessive increase in the supply pressure Pd-Pm of the cooling oil to the second stage compressor is also prevented, and the refrigerant dissolved in the cooling oil in the second stage compressor is prevented from causing a decrease in capacity. do.

In the above description, it is assumed that the calculation formula for determining the target value Pms of the intermediate pressure Pm does not change unless the set value Ts of the evaporation temperature Te of the refrigerant in the evaporator 6 is changed. It may be. However, for example, in the case where the evaporator 6 is arranged in the freezing warehouse, when the door is left open for carrying in and out of the load, the internal temperature, that is, the actual evaporation temperature Te rises rapidly, The differential pressure ΔP between the intermediate pressure Pmth and the suction pressure Ps may be larger than the lower limit differential pressure ΔPmin.

Therefore, even if the set value Ts of the evaporation temperature Te is constant, changing the expression of the target value Pms is an effective means for increasing the efficiency of the refrigerating device 1. In addition, it is also considered that it is preferable to change the set value Ts of the evaporation temperature Te of the refrigerant in the evaporator 6 by cascade control or the like.

In addition, in the above embodiment, since the mechanical compression ratio of the first stage compressor 2 and the mechanical compression ratio of the second stage compressor 3 are equal, the theoretical intermediate pressure Pmth = {√ (Ps · Pd)} is set. When the ratio of the mechanical compression ratio of the first stage compressor 2 and the mechanical compression ratio of the second stage compressor 3 is represented by a constant k, the theoretical intermediate pressure Pmth = {√ (Ps · Pd / k)} Becomes That is, in the present invention, the theoretical intermediate pressure Pmth is a value obtained by multiplying the square root of the product of the suction pressure Ps and the discharge pressure Pd by a constant √k.

1: refrigeration unit
2: first stage compressor
3: 2nd stage compressor
4: condenser
5: expansion valve
6: evaporator
7: refrigerant circulation flow path
8: first stage oil separator
9: 2nd stage oil separator
10: first stage oil passage
11: second stage oil passage
12: suction pressure detector (suction pressure detection means)
13: middle pressure detector (medium pressure detecting means)
14 discharge pressure detector (discharge pressure detecting means)
15: evaporation temperature detector (evaporation temperature detection means)
16: first stage control device (first stage control means)
17: second stage control device (second stage control means)

Claims (3)

The first stage compressor, the first stage oil separator, and the second stage compressor, the second stage oil separator, the condenser, the expansion valve, and the evaporator, which can be controlled independently of the first stage compressor, are provided in the refrigerant circulation passage. Intervention is made,
A first stage oil passage for refluxing the oil separated by the first stage oil separator to the first stage compressor,
A second stage oil passage for returning the oil separated by the second stage oil separator to the second stage compressor;
Suction pressure detecting means for detecting suction pressure of the first stage compressor;
Intermediate pressure detecting means for detecting a discharge pressure of the first stage compressor;
Discharge pressure detecting means for detecting a discharge pressure of the second stage compressor;
First stage control means for controlling the rotational speed of the first stage compressor in accordance with a refrigeration load;
The theoretical intermediate pressure is calculated from the square root of the product of the detected value of the suction pressure detecting means and the detected value of the discharge pressure detecting means,
When the difference between the theoretical intermediate pressure and the detected value of the suction pressure detecting means is greater than a predetermined lower limit differential pressure, the second intermediate compressor is configured to match the detected value of the intermediate pressure detecting means with the theoretical intermediate pressure. To control the speed,
When the difference between the theoretical intermediate pressure and the detected value of the suction pressure detecting means is equal to or less than the lower limit differential pressure, the detected value of the intermediate pressure detecting means is equal to the value obtained by adding the lower limit differential pressure to the detected value of the suction pressure detecting means. And a second stage control means for controlling the rotational speed of the second stage compressor. The method according to claim 1, further comprising evaporation temperature detection means for detecting an evaporation temperature of the evaporator,
And the first stage control means controls the rotation speed of the first stage compressor in accordance with the detected value of the evaporation temperature detection means. The refrigeration apparatus according to claim 1 or 2, wherein the first stage compressor and the second stage compressor each comprise a screw compressor.

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