JPH0771830A - Heat pump device - Google Patents

Abstract

PURPOSE:To regulate the amount of refrigerant to a proper amount by providing a gas-phase connection passage for introducing gas-phase refrigerant in a gas- liquid separator into a liquid receiver and a regulating valve for regulating the amount of the gas-phase refrigerant passing through the gas-phase connection passage. CONSTITUTION:A gas-phase connection passage (rp) fluidly connects gas-phase refrigerant from a gas-liquid separator 10 with gas-phase portion in a liquid receiver 12 to introduce gas-phase refrigerant Gh in the separator 10 into the receiver 12. A liquid-receiver regulating valve vR provided in the passage (rp) regulates the amount of the high pressure gas-phase refrigerant Gh introduced into the receiver 12 through the passage (rp) from the separator 10, whereby the liquid level of liquid-phase refrigerant L stored in the receiver 12 is regulated.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump device, and more particularly, to a gas-liquid separator for separating a high-pressure refrigerant fed from a high-pressure refrigerant delivery section into a gas-phase refrigerant and a liquid-phase refrigerant, and a gas-liquid separation thereof. Heat generating device provided with a heat generating condenser for condensing the vapor phase refrigerant sent from the evaporator, and a cold heat producing evaporator for evaporating the liquid phase refrigerant sent from the vapor-liquid separator after passing through the expansion means. Regarding

[0002]

2. Description of the Related Art FIG. 7 shows a refrigerant flow in a cold-heat parallel mode in which warm heat and cold heat are generated in parallel in a conventional apparatus. The two-phase refrigerant GL is fed to the gas-liquid separator 10, the high-pressure gas-liquid two-phase refrigerant GL is separated into the gas-phase refrigerant Gh and the liquid-phase refrigerant L in the gas-liquid separator 10, and the separation is performed. The gas-phase refrigerant Gh
From 0 to the hot heat generating condenser Ci to be condensed, the separated liquid phase refrigerant L is supplied from the gas-liquid separator 10 to the cold heat generating evaporator Ei via the expansion means exV to be evaporated.
As a result, heat for use in heating, reheating, article heating, etc. is generated in the heat generating condenser Ci, and cooling / dehumidifying / cooling is performed.
Cold heat for applications such as article cooling is generated by the cold heat generation evaporator Ei.

Further, in this cold-heat parallel mode, the liquid level of the stored liquid phase refrigerant L in the gas-liquid separator 10 is detected by the liquid level detection means 14a, and based on this detection information, the storage in the gas-liquid separator 10 is carried out. The amount of the liquid-phase refrigerant discharged from the gas-liquid separator 10 is controlled by the valve vL so as to keep the liquid level of the liquid-phase refrigerant L at a fixed level m.
The gas-liquid ratio of the gas-liquid two-phase refrigerant GL as the high-pressure refrigerant to be fed from the heat dissipation condenser Co as the high-pressure refrigerant delivery unit A to the gas-liquid separator 10 (in other words, Wetness or dryness), the heat generation condenser Ci
And the cold heat generation evaporator Ei are adjusted by adjusting the heat radiation capacity of the heat radiation condenser Co according to the operating state of each (for example, refer to JP-A-4-214153).

That is, in contrast to changing and adjusting the gas-liquid ratio of the gas-liquid two-phase refrigerant GL according to the operating states of the hot heat generating condenser Ci and the cold heat generating evaporator Ei, the stored liquid phase in the gas-liquid separator 10 is changed. By carrying out the adjustment control for keeping the liquid level of the refrigerant L at the fixed level m in parallel, only the gas phase refrigerant Gh is supplied to the hot heat generating condenser Ci and the liquid phase refrigerant L is supplied to the cold heat generating evaporator Ei.
Only the heat-generating condenser Ci and the cold-heat generating evaporator Ei are stably operated.

In the cold-heat parallel mode, the condensed liquid-phase refrigerant L sent from the heat-generating condenser Ci is combined with the separated liquid-phase refrigerant L in the gas-liquid separator 10 to form the expansion means exV. It is configured to be supplied to the cold heat generation evaporator Ei via the.

[0006]

In the heat pump device of this type having the gas-liquid separator 10, the heat exchanger used as the heat generation condenser Ci in the cold / heat parallel mode as described above is used as the second heat exchanger. A form that is switched and used as a cold heat generation evaporator Ei ′, or a heat generation condenser C
The refrigerant supply to i is cut off, and another second cold heat generation evaporator E
i ′ was used as the cold heat generation evaporator Ei in the cold heat only mode in which only cold heat is generated by the cold heat generation evaporator Ei and the second cold heat generation evaporator Ei ′, or in the cold / heat parallel mode. In a mode in which the heat exchanger is switched and used as the second heat-generating condenser Ci ', or in a mode in which the refrigerant supply to the cool-heat generating evaporator Ei is cut off and another second heat-generating condenser Ci' is used, In many cases, the warm-heat only mode in which only warm heat is generated by the warm-heat generating condenser Ci and the second warm-heat generating condenser Ci 'can be switched to the cold-heat parallel mode.

As shown in FIG. 8, the refrigerant flow when the above-mentioned cold heat only mode is carried out in the conventional apparatus is such that the condensed liquid phase refrigerant L is supplied from the heat radiating condenser Co as the high pressure refrigerant delivery section A to the high pressure refrigerant. The liquid-phase refrigerant L is supplied from the gas-liquid separator 10 to the cold-heat generating evaporator Ei and the second cold-heat generating evaporator Ei ′ through expansion means exV while being sent to the gas-liquid separator 10. Then, the gas-liquid separator 10 becomes a passage for only the liquid-phase refrigerant L in this cold heat only mode, and thus is in a full liquid state filled with the liquid-phase refrigerant L.

Further, the refrigerant flow in the case of carrying out the above-mentioned heating only mode in the conventional apparatus is as shown in FIG.
While the operation of the endothermic evaporator Eo is performed in place of the operation of the heat dissipation condenser Co, the compressor 6 serving as the high-pressure refrigerant delivery unit A supplies the high-pressure gas-phase refrigerant Gh as the high-pressure refrigerant to the gas-liquid separator 10. , The high-pressure gas-phase refrigerant Gh is supplied to the gas-liquid separator 10
From the heat-generating condenser Ci to the second heat-generating condenser Ci ′ to be condensed respectively, and in this heat-only mode, the gas-liquid separator 10 is operated only with the gas-phase refrigerant Gh. Since it becomes a passage, the liquid-phase refrigerant L
It becomes an empty state where there is no.

However, in the heat pump device in which the refrigerant is circulated by the compressor 6, the substantial amount (weight) of the refrigerant circulating in the refrigerant circuit, that is, the stored liquid phase in the gas-liquid separator 10 out of the refrigerant filled in the refrigerant circuit. The discharge pressure po and the suction pressure ps of the compressor 6 change depending on the amount (weight) of the refrigerant excluding the stagnant amount of the refrigerant, and the discharge pressure po and the suction pressure ps of the compressor 6 are set within appropriate ranges for operating the apparatus. Real amount of refrigerant suitable for keeping (hereinafter referred to as proper refrigerant amount)
Is a heat generating condenser Ci, Ci 'or a cold heat generating evaporator E.
There is a characteristic that changes with the change / change of the heat pump operation state including the change / change of the operation state of i and Ei ′.

In this respect, in the cold heat only mode shown in FIG. 8, since the gas-liquid separator 10 is in a full state, the liquid level of the stored liquid-phase refrigerant L in the gas-liquid separator 10 is set to the fixed position m. Maintained (in other words, the amount of liquid-phase refrigerant stored in the gas-liquid separator 10 is kept constant) Compared to the above-described cold-heat parallel mode, the actual amount of refrigerant circulating in the refrigerant circuit is reduced. Contrary to the decrease in the amount, in the normal cold / heat application such as cooling / heating, generally, the appropriate refrigerant amount in the cold / heat only mode tends to be larger than the appropriate refrigerant amount in the cold / heat parallel mode.

Further, in the single heating mode shown in FIG. 9, the gas-liquid separator 10 is in an empty state, so that the liquid level of the stored liquid-phase refrigerant L in the gas-liquid separator 10 is kept at the fixed position m. Compared with the cold / heat parallel mode, the amount of the actual refrigerant that circulates in the refrigerant circuit increases, but contrary to the increase in the amount of the actual refrigerant, in the normal cold / heat application such as cooling / heating, generally, the proper refrigerant in the single heating / heating mode is used. The amount tends to be smaller than the proper amount of refrigerant in the cold-heat parallel mode.

In the conventional apparatus, the cold heat alone mode or the warm heat alone mode as described above is executed by switching to the cold heat parallel mode, that is, a plurality of operation modes for changing the heat pump operating state by switching the refrigerant path are switched. In the implementation, a change in the actual refrigerant amount and the appropriate refrigerant amount such as a decrease in the actual refrigerant amount contrary to the increasing tendency of the appropriate refrigerant amount or an increase in the actual refrigerant amount contrary to the decreasing tendency of the appropriate refrigerant amount occurs. Since there is a difference between the actual refrigerant amount and the proper refrigerant amount, a pressure abnormality such as an abnormal increase in the compressor discharge pressure po or an abnormal decrease in the compressor suction pressure ps is apt to occur, and by the automatic There was a problem that the stop function was frequently activated to make the device inconvenient to use, or that malfunctions and device deterioration due to abnormal pressure were likely to occur.

It is an object of the present invention to make full use of the original advantages of the design and installation of this type of heat pump device using a gas-liquid separator, while the substantial amount of refrigerant circulated in the refrigerant circuit is determined by the gas-liquid separation. This is to enable adjustment to the proper refrigerant amount regardless of the change in the storage amount of the liquid-phase refrigerant in the container and the change in the appropriate refrigerant amount described above.

[0014]

[Means for Solving the Problems]

[First Characteristic Configuration] First of heat pump device according to the present invention
The characteristic configuration is a gas-liquid separator that separates the high-pressure refrigerant sent from the high-pressure refrigerant delivery unit into a gas-phase refrigerant and a liquid-phase refrigerant, and heat generation that condenses the gas-phase refrigerant sent from the gas-liquid separator. In a configuration in which a condenser and a cold heat generation evaporator that evaporates the liquid-phase refrigerant sent from the gas-liquid separator after passing through the expansion means are provided, the liquid-phase refrigerant sent from the gas-liquid separator is A liquid refrigerant passage leading to the expansion means, or a liquid receiver communicating with a liquid refrigerant passage leading the liquid phase refrigerant sent from the heat-generating condenser, and the gas phase refrigerant in the gas liquid separator with the liquid receiver. There is provided a gas-phase communication passage communicating with the gas-phase communication passage and a regulating valve for adjusting the amount of conduction of the gas-phase refrigerant in the gas-phase communication passage.

[Second Characteristic Configuration] A second characteristic structure of the heat pump device according to the present invention is a liquid amount detecting means for detecting a stored amount of the liquid phase refrigerant in the liquid receiver in the implementation of the first characteristic structure. In each of the plurality of operation modes in which the heat pump operation state is changed by switching the refrigerant path provided, the liquid amount of the liquid-phase refrigerant in the liquid receiver is set to the target storage amount set for each operation mode, The control means for adjusting the adjusting valve based on the detection information of the quantity detecting means is provided.

[Third Characteristic Configuration] A third characteristic configuration of the heat pump device according to the present invention is the pressure detecting means for detecting the discharge pressure or the suction pressure of the compressor for circulating the refrigerant in the implementation of the first characteristic configuration. And the control means for adjusting the adjusting valve based on the detection information of the pressure detecting means so that the discharge pressure or the suction pressure of the compressor becomes the target pressure.

[0017]

[Action]

[Operation of First Characteristic Configuration] That is, in the above-described first characteristic configuration (see FIG. 1), the liquid refrigerant passage rr for guiding the liquid phase refrigerant L sent from the gas-liquid separator 10 to the expansion means exV, or By providing the liquid receiver 12 that communicates with the liquid refrigerant passage rr 'that guides the liquid-phase refrigerant L sent from the heat-generating condenser Ci, the liquid receiver passages 12 have the basic functions of these liquid refrigerant passages rr, rr. The liquid-phase refrigerant L in 'is introduced into the receiver 12, and the introduced liquid-phase refrigerant L is stored in the receiver 12.

When the liquid phase refrigerant L is stored in the liquid receiver 12, the gas phase refrigerant Gh in the gas phase communication passage rp is stored.
Of the high-pressure gas-phase refrigerant Gh introduced from the gas-liquid separator 10 to the liquid receiver 12 is increased by adjusting the conduction amount of the liquid-phase refrigerant to the liquid-side refrigerant in the liquid receiver 12. As a situation in which the amount of introduction of the gas-phase refrigerant Gh from the gas-phase communication passage rp is larger than the amount of the gas-phase refrigerant Gh that is liquidized in a form absorbed in L, the stored liquid-phase refrigerant in the liquid receiver 12 L is sent out from the liquid receiver 12 in a form of being pushed out by the introduced gas-phase refrigerant Gh, whereby the storage amount of the liquid-phase refrigerant L in the liquid receiver 12 is adjusted to the decreasing side, and is circulated in the refrigerant circuit. The amount of refrigerant (weight) is adjusted to the increasing side.

On the contrary, the amount of conduction of the gas-phase refrigerant Gh in the gas-phase communication passage rp is adjusted to the decreasing side by the adjusting valve vR,
By reducing the amount of high-pressure gas-phase refrigerant Gh introduced from the gas-liquid separator 10 to the liquid receiver 12, a gas-phase refrigerant that is liquefied in the liquid receiver 12 in the form of being absorbed in the liquid-phase refrigerant L G
As a situation in which the amount of h becomes larger than the amount of introduction of the vapor phase refrigerant Gh from the vapor phase communication passage rp, the liquid refrigerant passage rr,
The liquid-phase refrigerant L is introduced into the liquid receiver 12 from rr 'so that the amount of the liquid-phase refrigerant L stored in the liquid receiver 12 is adjusted to the increasing side and circulated in the refrigerant circuit. The actual refrigerant amount (weight) is adjusted to the decreasing side.

Although FIG. 1 shows an operation mode in which a high-pressure gas-liquid two-phase refrigerant GL is supplied as a high-pressure refrigerant to the gas-liquid separator 10 from the heat radiating condenser Co serving as the high-pressure refrigerant delivery section A, the cold heat described above is used. In a single mode or the like, a high-pressure liquid-phase refrigerant L as a high-pressure refrigerant from the heat-radiating condenser Co as the high-pressure refrigerant delivery unit A
Even in the operating mode in which the gas is sent to the gas-liquid separator 10, if the temperature and pressure of the high-pressure liquid-phase refrigerant L are appropriately adjusted by adjusting the heat dissipation capacity of the heat dissipation condenser Co, etc., it is received via the gas phase communication passage rp. High-pressure gas-phase refrigerant Gh for adjusting storage amount to be sent to the liquid container 12
Can be generated in the gas-liquid separator 10.

[Operation of Second Characteristic Configuration] In the second characteristic configuration (see FIGS. 1 to 5), the storage amount of the liquid-phase refrigerant L in the liquid receiver 12 is adjusted by adjusting the adjusting valve vR. , In adjusting the substantial amount of refrigerant circulating in the refrigerant circuit, the substantial amount of refrigerant circulating in the refrigerant circuit becomes an appropriate amount of refrigerant for each of a plurality of operation modes in which the refrigerant pump is switched to change the heat pump operating state. In this way (in other words, the discharge pressure po of the compressor 6 and the suction pressure ps are in the proper range), the liquid-phase refrigerant storage amount of the liquid receiver 12 is set as the target storage amounts n1 to n5, and used in experiments and test operations. It is set in advance based on this.

In each operation mode, the liquid receiver 1
The storage amount of the liquid-phase refrigerant L in the liquid receiver 12 is adjusted at that time by adjusting the adjusting valve vR by the control means 13 based on the detection information of the liquid-amount detecting means 14b that detects the liquid-phase refrigerant storage amount of No. 2. The above target storage amount n1 for the operation mode
.About.n5, whereby the substantial amount of refrigerant circulating in the refrigerant circuit in each operation mode is automatically adjusted to the appropriate amount of refrigerant in each operation mode.

[Operation of Third Characteristic Configuration] In the third characteristic configuration (see FIG. 6), the storage amount of the liquid phase refrigerant L in the liquid receiver 12 is adjusted by adjusting the adjusting valve vR, and the refrigerant circuit is formed. In adjusting the amount of the actual refrigerant that circulates inside,
Discharge pressure p of the compressor 6 that changes depending on the substantial amount of refrigerant
Adjustment valve vR with o and suction pressure ps itself as adjustment indexes
Adjust.

That is, the discharge pressure po of the compressor 6 is adjusted by adjusting the adjusting valve vR by the control means 13 based on the detection information of the pressure detection means P1 and P2 for detecting the discharge pressure po of the compressor 6 or the suction pressure ps. Alternatively, the liquid-phase refrigerant storage amount in the liquid receiver 12 is adjusted so that the suction pressure ps becomes the target pressure (in other words, the actual refrigerant amount becomes the proper refrigerant amount in the heat pump operating state at that time). The actual amount of refrigerant in the refrigerant circuit is adjusted by this, and thereby the discharge pressure po or the suction pressure ps of the compressor is automatically adjusted to the target pressure.

[0025]

【The invention's effect】

[Effects of First Characteristic Configuration] That is, according to the first characteristic configuration of the present invention, even if the liquid level of the stored liquid phase refrigerant in the gas-liquid separator changes in switching between a plurality of operation modes. In addition, even if the proper amount of refrigerant that can maintain the discharge pressure or suction pressure of the compressor within the proper range changes, the amount of liquid-phase refrigerant stored in the receiver is adjusted by adjusting the adjustment valve, By adjusting the substantial amount of the refrigerant that circulates, the actual amount of the refrigerant when the operation modes are performed can be adjusted to the appropriate amount of the refrigerant in the operation mode.

Moreover, according to the first characteristic configuration of the present invention,
Not only can the operation mode switching that accompanies the liquid level change of the stored liquid phase refrigerant in the gas-liquid separator be handled as described above, but also the change of the heat pump operating state that does not accompany the liquid level change of the stored liquid phase refrigerant in the gas-liquid separator. Or change (for example, operation mode switching without a liquid level change of the stored liquid phase refrigerant in the gas-liquid separator, or the operation mode itself is the same, but the operating conditions of the heat generation condenser and the heat generation evaporator change Therefore, even if only the proper amount of refrigerant changes, the amount of liquid-phase refrigerant stored in the liquid receiver can be adjusted by adjusting the adjustment valve in an appropriate form, and thereby circulating in the refrigerant circuit. By adjusting the substantial amount of refrigerant, the actual amount of refrigerant in each heat pump operating state can be adjusted to the proper amount of refrigerant in the actual operating state.

From the above, it is possible to effectively prevent a pressure abnormality such as an abnormal increase in the compressor discharge pressure or an abnormal decrease in the compressor suction pressure in a heat pump device of this type using a gas-liquid separator. As a result, the frequency of automatic stop of the device due to the pressure abnormality can be reduced to improve the usability of the device, and the device deterioration due to the pressure abnormality can be prevented to improve the service life of the device.

In this type of heat pump device using a gas-liquid separator, the gas-liquid separator, the heat-generating condenser and the cold-generating evaporator are installed indoors, whereas the high-pressure refrigerant delivery section is constituted. It is often used in an installation form in which the compressor, the heat dissipation condenser, and the endothermic evaporator are used as an outdoor installation device, and in this indoor and outdoor separation installation form, the outdoor installation device side is installed indoors. One where a gas-liquid two-phase refrigerant is sent to a gas-liquid separator, where two separate refrigerant pipes are usually required to simultaneously send a high-pressure gas-phase refrigerant and a liquid-phase refrigerant to the device side It has the advantage of being able to use only the refrigerant pipes, that is, the advantage that the number of refrigerant pipes extending over the outdoor side and the indoor side can be reduced.

In this respect, according to the first characteristic configuration of the present invention,
The liquid receiver is connected to the liquid refrigerant path for guiding the liquid phase refrigerant sent from the gas-liquid separator to the expansion means or the liquid refrigerant path for guiding the liquid phase refrigerant sent from the heat-generating condenser, and the receiver Since the liquid and gas-liquid separator is configured to be connected via a gas-phase communication passage, by using the liquid receiver as the indoor-side installation device together with the gas-liquid separator in the above-mentioned indoor-outdoor installation configuration, The first characteristic configuration of the present invention can be easily implemented only by improving the indoor installation device side, and the number of refrigerant pipes extending over the indoor side and the outdoor side can be reduced.
It is possible to make full use of the original advantages of the design and installation of this type of heat pump device.

[Effects of Second Characteristic Configuration] In the implementation of the first characteristic structure described above, if the second characteristic structure of the present invention is adopted, an operation mode involving a change in the liquid level of the stored liquid phase refrigerant in the gas-liquid separator. Whether it is switching or operation mode switching without such a liquid level change,
In switching between a plurality of operation modes that change the refrigerant path to make the heat pump operating state different,
By adjusting the adjustment valve by the control means, the actual refrigerant amount is automatically adjusted to the proper refrigerant amount in each operation mode, and the pressure generated by the difference between the actual refrigerant amount and the proper refrigerant amount due to the switching of the operation modes. Abnormality is surely prevented.

[Effect of Third Characteristic Configuration] In implementing the first characteristic structure, if the third characteristic structure of the present invention is adopted, not only the operation mode is changed but also the heat-generating condenser is used in the same operation mode. The discharge pressure of the compressor can be adjusted by adjusting the adjustment valve by the control means even when the operating condition of the heat pump operating condition of the heat and cold heat generating evaporator changes or is changed intentionally due to external factors. Alternatively, by automatically adjusting the suction pressure to the target pressure, it is possible to reliably prevent the pressure abnormality that occurs due to the difference between the actual refrigerant amount and the proper refrigerant amount due to the change / change of the heat pump operating state.

[0032]

EXAMPLES Next, examples will be described.

FIG. 1 shows a separate type air conditioner, 1 is an outdoor unit, 2 is an indoor unit, and these outdoor unit 1 and indoor unit 2
Is the two high-pressure side and low-pressure side transition refrigerant pipes 3a, 3b
It is connected with.

The outdoor unit 1 mainly includes an outdoor heat exchanger 4 for absorbing and releasing heat from the outdoor air OA, an outdoor fan 5 for ventilating the outdoor air OA to the outdoor heat exchanger 4, and a compressor 6. It is equipped.

In the indoor unit 2, the upstream heat exchanger 7, the downstream heat exchanger 8 located downstream of the upstream heat exchanger 7 in the air flow direction, and the upstream / downstream heat exchangers 7, 8 were adjusted. An air supply fan 9, a gas-liquid separator 10, a subcooler 11, a liquid receiver 12, first to third expansion valves ex1 to ex3, a flow rate adjusting valve vF, which supplies the air SA to a corresponding air-conditioning target area. In addition, the liquid receiver adjusting valve vR is equipped as a main device.

The first to third expansion valves ex1 to ex
3 has a structure capable of switching between a state in which it functions as an original expansion means, a state in which it functions as a flow rate adjusting valve, and a state in which it functions as a flow path opening / closing valve.

Reference numeral 13 is a controller for controlling the operation of the air conditioner, and in the figure, v1 to v8 are solenoid valves for switching the refrigerant path according to the operation mode, and c1 and c2 are check valves. .

In FIG. 1, the upstream heat exchanger 7 functions as a cold heat generating evaporator Ei to cool and dehumidify the passing air, and the downstream heat exchanger 8 functions as a warm heat generating condenser Ci. Reheat the cooling dehumidified air from 7
On the other hand, the "dehumidifying and cooling mode" in which the outdoor heat exchanger 4 functions as the heat radiating condenser Co to radiate heat to the outside air OA
It shows the refrigerant flow state in the (operation mode corresponding to the above-mentioned cold-heat parallel mode), and specifically radiates the high-pressure gas-phase refrigerant Gh (indicated by a thick black line in the figure) discharged from the compressor 6. Partly condensing with the outdoor heat exchanger 4 as the condenser Co,
Then, the outdoor heat exchanger 4 as the radiation condenser Co is used as the high-pressure refrigerant delivery section A for the gas-liquid separator 10 on the indoor unit side, and the high-pressure gas-liquid two-phase delivered from the outdoor heat exchanger 4 is used. A refrigerant GL (indicated by a thick line with thick hatching in the figure) is sent to the gas-liquid separator 10 via the high-pressure side crossover pipe 3a, and the gas-liquid two-phase refrigerant GL supplied in this gas-liquid separator 10 is supplied. Is separated into a high pressure gas phase refrigerant Gh and a liquid phase refrigerant L.

The high-pressure gas-phase refrigerant Gh (thick black line) separated in the gas-liquid separator 10 is supplied to the downstream heat exchanger 8 as the heat-generating condenser Ci via the gas-phase refrigerant passage rh to be condensed, and then downstream. The liquid-phase refrigerant L sent from the heat exchanger 8 (indicated by a thin hatched thick line in the drawing) is the second liquid-refrigerant passage rr ′ that guides the liquid-phase refrigerant L sent from the heat-generating condenser Ci. The liquid-phase refrigerant L introduced into the liquid receiver 12 via the connection path r2 and separated in the gas-liquid separator 10 is the delivery liquid-phase refrigerant L from the gas-liquid separator 10 (thick line with thin hatching). It is introduced into the liquid receiver 12 through the fourth connection passage r4 as the liquid refrigerant passage rr leading to the expansion means exV, and
The liquid-phase refrigerant L introduced into the liquid receiver 12 is supplied to the liquid receiver 12
To the upstream heat exchanger 7 as the cold heat generating evaporator Ei via the first connection path r1 to the first connection path r1 and the first expansion valve ex1 that functions as the original expansion means exV in the first connection path r1. Let

Further, the vaporized low-pressure vapor-phase refrigerant Gc sent from the upstream heat exchanger 7 (indicated by a thick white line in the figure)
Is returned to the suction side of the compressor 6 through the cooling refrigerant passage rc, the subcooler 11 inside the gas-liquid separator 10, and the low-pressure side transition refrigerant pipe 3b (note that the black-painted valve in the figure). Indicates a valve closed state).

Reference numeral 14a is a first liquid level sensor for detecting the liquid level of the stored liquid phase refrigerant L in the gas-liquid separator 10, and in the above "dehumidifying and cooling mode", the controller 13 controls the first liquid level sensor 14a. Based on the detection information, the output of the outdoor fan 5 is adjusted to adjust the heat dissipation capacity of the outdoor heat exchanger 4 as the heat dissipation condenser Co to adjust the degree of condensation of the refrigerant in the outdoor heat exchanger 4. In order to adjust and maintain the liquid level of the stored liquid phase refrigerant L in 10 to the set liquid level m, the gas-liquid ratio of the gas-liquid two-phase refrigerant GL sent from the outdoor heat exchanger 4 to the gas-liquid separator 10 (in other words, For example, adjust the wetness or dryness of the high-pressure wet steam refrigerant.

Rp is the gas-phase refrigerant passage r from the gas-liquid separator 10.
h is a gas-phase communication passage that connects the gas-phase portion of the liquid receiver 12 and allows the gas-phase refrigerant Gh in the gas-liquid separator 10 to conduct to the liquid receiver 12, and this gas-phase communication passage rp and The installed receiver adjustment valve vR adjusts the amount of high-pressure gas-phase refrigerant Gh introduced from the gas-liquid separator 10 into the receiver 12 via the gas-phase communication passage rp by the receiver adjustment valve vR. Thus, a storage amount adjusting means for adjusting the liquid level of the stored liquid phase refrigerant L in the liquid receiver 12 (in other words, the amount of storage of the liquid phase refrigerant L in the liquid receiver 12) is configured, and control is performed for this. The liquid receiver 13 receives the liquid receiver 1 based on the detection information of the second liquid level sensor 14b that detects the liquid level of the liquid refrigerant L in the liquid receiver 12.
The liquid level of the stored liquid phase refrigerant L in 2 is set to "dehumidification cooling mode"
So as to adjust and maintain the set target liquid level x1 (in other words, to adjust and maintain the stored amount of the liquid phase refrigerant L in the receiver 12 to the set target stored amount n1 for the "dehumidifying and cooling mode"). 2), the liquid receiver adjusting valve vR is adjusted.

In the subcooler 11, the cooling refrigerant passage r
low-pressure gas-phase refrigerant G from the upstream heat exchanger 7 guided by c
c and the separated liquid phase refrigerant L in the gas-liquid separator 10 are heat-exchanged to cool the separated liquid phase refrigerant L in the gas-liquid separator 10, whereby the separated liquid phase refrigerant L serves as the expansion means exV. When the gas is sent to the expansion valve ex1, it is possible to prevent a part of the gas phase from being generated in the separated liquid phase refrigerant L in the middle of the process (particularly in the passing process of the flow rate adjusting valve vF that causes decompression to some extent).

In the "dehumidifying and cooling mode", the flow rate adjusting valve v
F indicates that the opening degree of the second expansion valve ex2 is adjusted as a flow rate adjusting valve in accordance with the required heat generation amount of the downstream heat exchanger 8 serving as the heat generation condenser Ci, while the downstream heat from the gas-liquid separator 10 is adjusted. The flow path resistance of the system that reaches the liquid receiver 12 via the exchanger 8 and the flow path resistance of the system that directly reaches the liquid receiver 12 from the gas-liquid separator 10 via the fourth connection path r4 are approximately The opening degree is adjusted by the controller 13 so as to be equal to each other, so that the liquid-phase refrigerant L from the downstream heat exchanger 8 and the liquid-phase refrigerant L from the gas-liquid separator 10 are joined at the liquid receiver 12. Smooth out.

In FIG. 2, the upstream heat exchanger 7 is connected to the cold heat generation evaporator Ei with the refrigerant supply to the downstream heat exchanger 8 cut off.
To control the cooling temperature of the passing air,
The refrigerant | coolant flow state of the "normal cooling mode" which makes the outdoor heat exchanger 4 function as a heat radiation condenser Co, and heat-radiates with respect to the external air OA is shown, and, specifically, the high pressure gas-phase refrigerant Gh (discharged from the compressor 6 (Black thick line) is condensed in the outdoor heat exchanger 4 as the heat radiating condenser Co, and the outdoor heat exchanger 4 as the heat radiating condenser Co is separated into gas and liquid on the indoor unit side as in the “dehumidifying and cooling mode”. The high-pressure refrigerant delivery section A for the vessel 10 is used as a high-pressure liquid-phase refrigerant L (thin line with fine hatching) delivered from the outdoor heat exchanger 4 through the high-pressure side connecting pipe 3a to form a gas-liquid separator. Send to 10.

The liquid-phase refrigerant L supplied to the gas-liquid separator 10 is
The fourth connection path r4, the liquid receiver 12, the first connection path r1,
And the original expansion means ex in the first connecting path r1
It is supplied to the upstream heat exchanger 7 as the cold heat generation evaporator Ei via the first expansion valve ex1 which functions as V and is evaporated here.

The evaporated low-pressure vapor-phase refrigerant Gc (white thick line) sent from the upstream heat exchanger 7 is the cooling refrigerant passage rc, the supercooler 11, and the same as in the "dehumidifying and cooling mode". , Is returned to the suction side of the compressor 6 via the low-pressure side transition refrigerant pipe 3b.

In this "normal cooling mode", the controller 1
3 is a mode in which a part of the gas-phase refrigerant Gh is generated from the high-pressure liquid-phase refrigerant L supplied in the gas-liquid separator 10, and the liquid level of the stored liquid-phase refrigerant L in the gas-liquid separator 10 is set to the set liquid level m. In order to adjust and maintain the heat dissipation condenser C by adjusting the output of the outdoor fan 5 based on the detection information of the first liquid level sensor 14a.
The heat dissipation capacity of the outdoor heat exchanger 4 as o is adjusted, the degree of supercooling of the liquid-phase refrigerant L sent from the outdoor heat exchanger 4 to the gas-liquid separator 10 is adjusted, and in the gas-liquid separator 10. In the mode in which the generated high-pressure vapor-phase refrigerant portion Gh is used for adjusting the liquid level of the liquid receiver, the controller 13 detects the liquid level by the second liquid level sensor 14b and the stored liquid-phase refrigerant L in the liquid receiver 12 is detected.
So that the liquid level of the liquid phase refrigerant L is adjusted and maintained at the set target liquid level x2 for the "normal cooling mode" (in other words, the storage amount of the liquid-phase refrigerant L in the receiver 12 is set for the "normal cooling mode". Adjusting and maintaining the stored amount n2), liquid receiver adjustment valve v
Adjust R.

In the gas-liquid separator 10, as in the "dehumidifying and cooling mode", the low-temperature low-pressure gas-phase refrigerant Gc sent from the upstream heat exchanger 7 as the cold heat generating evaporator Ei is used as the cooling refrigerant. The supercooling degree of the separated liquid-phase refrigerant L is increased by cooling the liquid-phase refrigerant in the supercooler 11 described above, whereby the liquid-phase refrigerant L sent to the first expansion valve ex1 as the expansion means exV.
Prevents the formation of some gas phase inside.

In FIG. 3, the upstream heat exchanger 7 is connected to the heat generating condenser Ci while the refrigerant supply to the downstream heat exchanger 8 is cut off.
To control the heating temperature of the passing air,
The refrigerant | coolant flow state of the "normal heating mode" which makes the outdoor heat exchanger 4 function as an endothermic evaporator Eo, and absorbs heat from the outdoor air OA is shown, and specifically, the compressor 6 with respect to the gas-liquid separator 10 on the indoor unit side is shown. The high-pressure refrigerant Gh (black thick line) discharged from the compressor 6 in the form of the high-pressure refrigerant delivery section A.
Is supplied to the upstream heat exchanger 7 as the heat-generating condenser Ci via the high-pressure side refrigerant pipe 3a, the gas-liquid separator 10 and the gas-phase refrigerant passage rh, and is condensed in the upstream heat exchanger 7.

Liquid phase refrigerant L delivered from the upstream heat exchanger 7.
(Thin line with thin hatching) indicates the heat generation condenser Ci
The first connection path r1 as a liquid refrigerant path rr 'that guides the delivery liquid phase refrigerant L from, the liquid receiver 12, the third connection path r3 in which the third expansion valve ex3 functions as the original expansion means exV, and the low pressure The low-pressure gas-phase refrigerant Gc (which is supplied to the outdoor heat exchanger 4 as the endothermic evaporator Eo through the side-passing refrigerant pipe 3b to be evaporated in the outdoor heat exchanger 4 and is sent from the outdoor heat exchanger 4 ( Return the white thick line) to the suction side of the compressor 6.

In the "normal heating mode", the gas-liquid separator 10 serving as a passage for the high-pressure gas-phase refrigerant Gh delivered from the compressor 6 is in an empty state in which no liquid-phase refrigerant is present. The control for adjusting the state of the refrigerant sent to the separator 10 based on the detection information of the first liquid level sensor 14a, such as the above-mentioned "dehumidifying cooling mode" or "normal cooling mode", stops, but the controller 13 In the mode in which the high-pressure gas-phase refrigerant Gh partially flowing from the gas-phase refrigerant passage rh to the gas-phase communication passage rp is used for adjusting the liquid receiver liquid level, the liquid receiver is detected based on the liquid level detection by the second liquid level sensor 14b. In order to adjust and maintain the liquid level of the stored liquid-phase refrigerant L in 12 to the set target liquid level x3 for the "normal heating mode" (in other words, the storage amount of the liquid-phase refrigerant L in the receiver 12 is "normal"). Adjust to set target storage amount n3 for "heating mode" As lifting), receiver control valve vR
Adjust.

FIG. 4 shows the refrigerant flow state in the "strong cooling mode" (the operation mode corresponding to the above-mentioned cooling / heating only mode),
The second expansion valve ex2 functions as the original expansion means exV together with the first expansion valve ex1, and the downstream heat exchanger 8 functions as the cold heat generation evaporators Ei, Ei ′ together with the upstream heat exchanger 7, and The liquid level of the stored liquid phase refrigerant L in the liquid receiver 12 is adjusted and maintained at the set target liquid level x4 for the "strong cooling mode" as the adjustment of the liquid receiver adjustment valve vR based on the detection information of the two liquid level sensor 14b. To do (in other words,
Except for adjusting the receiver adjustment valve vR so that the amount of the liquid refrigerant L stored in the receiver 12 is adjusted and maintained at the set target storage amount n4 for the "strong cooling mode"), the above description is made. This is the same as the "normal cooling mode" of.

FIG. 5 shows the refrigerant flow state in the “strong heating mode” (the operation mode corresponding to the above-mentioned heating only mode), in which the downstream heat exchanger 8 together with the upstream heat exchanger 7 are heated by the heat generation condenser Ci, Point to function as Ci ', and second
Liquid receiver adjusting valve vR based on the detection information of the liquid level sensor 14b
In order to adjust the above, the liquid level of the stored liquid phase refrigerant L in the liquid receiver 12 is adjusted and maintained at the set target liquid level x5 for the "strong heating mode" (in other words, the liquid phase refrigerant in the liquid receiver 12 is adjusted. L storage amount is set target storage amount n for "strong heating mode"
5) so that the liquid receiver adjustment valve vR is adjusted, so that it is the same as the above-mentioned “normal heating mode”.

In each of the above operation modes, the target liquid levels x1 to x5 (target storage amounts n1 to n5), which are targets of the liquid level adjustment (reservation amount adjustment) by the receiver adjustment valve vR, are set for each operation mode. In addition, the liquid in the liquid receiver 12 such that the discharge pressure po and the suction pressure ps of the compressor 6 are within appropriate ranges (that is, the substantial amount of refrigerant circulating in the refrigerant circuit is the appropriate amount of refrigerant described above). The phase refrigerant liquid level (liquid phase refrigerant storage amount) is obtained by experiment or trial operation, and these are set as target liquid levels x1 to x5 (target storage amounts n1 to n5) in each operation mode. On the other hand, as described above, in each operation mode, the liquid level (storage amount) of the liquid phase refrigerant L in the liquid receiver 12 is adjusted by adjusting the liquid receiver adjustment valve vR based on the detection information of the second liquid level sensor 14b. Setting target liquid level x1 to x (Set target storage amount n1~n5)
The automatic adjustment to prevent the occurrence of a pressure abnormality such as an abnormal increase in the compressor discharge pressure po and an abnormal decrease in the compressor suction pressure ps.

[Other Embodiments] Next, other embodiments will be listed.

(1) The liquid receiver 12 in the above-described embodiment.
To detect the storage amount of the liquid-phase refrigerant L in the liquid receiver 1
Although the mode of detecting the liquid level of the liquid-phase refrigerant L in 2 is adopted, the detection of the stored amount is not limited to the mode of detecting the liquid level, and various detection modes can be adopted. A means for detecting the stored amount of the liquid phase refrigerant L in the liquid receiver 12 including the two-liquid level sensor 14b is referred to as a liquid amount detecting means 14b.

(2) As in the above-described embodiment, based on the detection information of the liquid phase refrigerant storage amount (liquid level) in the liquid receiver 12, the liquid phase refrigerant storage amount (liquid level) in the liquid receiver 12 in each operation mode. ) Is the target storage amount n1 set for each operation mode
Instead of the control mode in which the receiver adjustment valve vR is adjusted so that it becomes n5 (target liquid level x1 to x5), the receiver adjustment valve vR using the discharge pressure po of the compressor 6 or the suction pressure ps itself as an adjustment index. It is also possible to adopt a control mode that adjusts.

That is, as shown in FIG. 6, pressure detecting means P1 for detecting the discharge pressure po of the compressor 6 or pressure detecting means P2 for detecting the suction pressure ps of the compressor 6 is provided, and these pressure detecting means are provided. A configuration may be adopted in which the controller 13 automatically adjusts the liquid receiver adjustment valve vR so that the discharge pressure po or the suction pressure Ps of the compressor 6 becomes the target pressure based on the detection information of P1 and P2. .

As in the controller 13 described above, the amount of the liquid-phase refrigerant stored in the liquid receiver 12 detected by the liquid amount detecting means 14b and the discharge of the compressor 6 detected by the pressure detecting means P1 and P2. The means for automatically adjusting the liquid receiver adjustment valve vR based on the suction pressures po, ps, etc. is collectively referred to as the control means 13.

(3) As a mode of adjusting the liquid receiver adjustment valve vR, for a specific operation mode among a plurality of operation modes, the liquid receiver 12 is detected based on the detection information of the amount of liquid refrigerant stored in the liquid receiver 12. Control means 1 so that the liquid-phase refrigerant storage amount of the target storage amount set for the operation mode is
3, the receiver adjusting valve vR is automatically adjusted, and for operating modes other than the specific mode described above, the detection information of the pressure detecting means P1 and P2 for detecting the discharge pressure po or the suction pressure ps of the compressor 6 is used. Based on this, a configuration may be adopted in which the control means 13 automatically adjusts the liquid receiver adjustment valve vR so that the discharge pressure po or the suction pressure Ps of the compressor 6 becomes the target pressure.

(4) As the adjustment mode of the receiver adjustment valve vR, the liquid refrigerant storage of the receiver 12 is based on the detection information of the liquid refrigerant storage amount in the receiver 12 at the start of each operation mode. The control means 13 automatically adjusts the receiver adjustment valve vR so that the amount becomes the target storage amount set for the operation mode, and thereafter, the discharge pressure p of the compressor 6 is adjusted.
o or pressure detecting means P1, P2 for detecting the suction pressure ps
A configuration may be adopted in which the liquid receiver adjusting valve vR is automatically adjusted by the control means 13 so that the discharge pressure po or the suction pressure Ps of the compressor 6 becomes the target pressure based on the detection information.

(5) The liquid receiver 12 guides the liquid-phase refrigerant L from the gas-liquid separator 10 to the expansion means exV.
And the fluid refrigerant passage rr 'for guiding the delivery liquid phase refrigerant L from the heat-generating condenser Ci may be separately provided. For a device in which the liquid-phase refrigerant is constantly delivered, a configuration is adopted in which the liquid receiver 12 is communicated only with the liquid refrigerant passage rr that guides the delivered liquid-phase refrigerant L from the gas-liquid separator 10 to the expansion means exV, or In the device in which the liquid-phase refrigerant is constantly delivered from the heat-generating condenser Ci, the liquid receiver 12 is communicated only with the liquid-refrigerant passage rr 'that guides the delivered liquid-phase refrigerant L from the heat-generating condenser Ci. You may adopt it.

(6) The above-mentioned embodiment shows an example in which the present invention is applied to a heat pump device for switching and operating a plurality of operation modes. The first and third characteristic configurations of the present invention are The present invention can also be applied to a heat pump device that does not switch modes, that is, a heat pump device that does not change the operating state by switching the refrigerant path.

(7) The use of the heat generated by the heat-generating condenser Ci is not limited to air-conditioning such as heating or reheating of dehumidified air for cooling, but may be used for heating or keeping heat of an article. It may be. In addition, the cold heat generation evaporator E
The application of the generated cold heat by i is not limited to the air conditioning application such as cooling and dehumidification of air, and may be any application such as cooling and keeping heat of an article.

It should be noted that reference numerals are given in the claims for convenience of comparison with the drawings, but the present invention is not limited to the configurations of the accompanying drawings by the entry.

[Brief description of drawings]

FIG. 1 is a refrigerant circuit diagram showing a refrigerant flow in a dehumidifying and cooling mode.

FIG. 2 is a refrigerant circuit diagram showing a refrigerant flow in a normal cooling mode.

FIG. 3 is a refrigerant circuit diagram showing a refrigerant flow in a normal heating mode.

FIG. 4 is a refrigerant circuit diagram showing a refrigerant flow in strong cooling mode.

FIG. 5 is a refrigerant circuit diagram showing a refrigerant flow in the strong heating mode.

FIG. 6 is a refrigerant circuit diagram showing another embodiment.

FIG. 7 is a refrigerant circuit diagram showing a refrigerant flow in a cold-heat parallel mode in a conventional device.

FIG. 8 is a refrigerant circuit diagram showing a refrigerant flow in a cold heat only mode in a conventional device.

FIG. 9 is a refrigerant circuit diagram showing a refrigerant flow in a heating only mode in a conventional device.

[Explanation of Codes] A high-pressure refrigerant delivery section Ci hot-heat generating condenser Ei cold-heat generating evaporator exV expansion means Gh gas-phase refrigerant GL, L high-pressure refrigerant L liquid-phase refrigerant n1 to n5 target storage amount P1, P2 pressure detection means po discharge Pressure ps Suction pressure rp Gas phase communication passage rr, rr 'Liquid refrigerant passage vR Adjustment valve 6 Compressor 10 Gas-liquid separator 12 Liquid receiver 13 Control means 14b Liquid amount detection means

Claims (3)

[Claims] 1. A gas-liquid separator (10) for separating high-pressure refrigerant (GL), (L) fed from a high-pressure refrigerant delivery section (A) into a gas-phase refrigerant (Gh) and a liquid-phase refrigerant (L). ) And the gas-phase refrigerant (G
a heat-generating condenser (Ci) for condensing h), and a liquid-phase refrigerant (L) delivered from the gas-liquid separator (10)
A heat pump device provided with a cold heat generation evaporator (Ei) for evaporating after passing the expansion means (exV) to a liquid phase refrigerant (L) sent from the gas-liquid separator (10).
Receiving liquid communicating with a liquid refrigerant passage (rr) that guides the refrigerant to the expansion means (exV) or a liquid refrigerant passage (rr ′) that guides the liquid-phase refrigerant (L) sent from the heat-generating condenser (Ci). (12), a gas-phase communication passage (rp) for conducting the gas-phase refrigerant (Gh) in the gas-liquid separator (10) to the liquid receiver (12), and a gas phase in the gas-phase communication passage (rp) A heat pump device provided with an adjusting valve (vR) for adjusting the amount of conduction of the refrigerant (Gh). 2. A plurality of operation modes in which a liquid amount detecting means (14b) for detecting a stored amount of the liquid-phase refrigerant (L) in the liquid receiver (12) is provided, and a refrigerant path is switched to change a heat pump operating state. In each of them, the liquid receiver (12)
Based on the detection information of the liquid amount detection means (14b), the adjustment valve (vR) so that the storage amount of the liquid-phase refrigerant (L) in (1) becomes the target storage amount (n1 to n5) set for each operation mode. The heat pump device according to claim 1, further comprising a control means (13) for adjusting 3. Pressure detecting means (P1), (P2) for detecting a discharge pressure (po) or a suction pressure (ps) of a compressor (6) for circulating a refrigerant is provided, Based on the detection information of the pressure detection means (P1) and (P2), the adjustment valve (v) is adjusted so that the discharge pressure (po) or the suction pressure (ps) becomes the target pressure.
The heat pump device according to claim 1, further comprising a control means (13) for adjusting R).