JP2002168534A - Heat pump system of air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat pump system of air conditioner which can prevent the compression of liquid even at low outside air temperature or at start of a compressor 2 after being left alone for a long period without enlarging an accumulator 10. SOLUTION: The accumulator 10 or a refrigerant passage 20 on suction side between the compressor 2 and the accumulator 10 is provided with an evaporation acceleration means 30 for gasifying a liquid refrigerant. As a result, the liquid refrigerant is gasified within the accumulator 10 or just before being sucked in the compressor, so this air conditioner can prevent the liquid compression at start of the compressor without enlarging the accumulator.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat pump air conditioner for cooling and heating, and more particularly to a heat pump air conditioner in which a refrigerant in a refrigerant circuit is circulated by a compressor driven by a water-cooled engine. It is suitable.

[0002]

2. Description of the Related Art In a conventional heat pump air conditioner, when a heat pump cycle is performed for cooling and heating, refrigerant returning to a compressor is separated into gas and liquid by an accumulator, and only refrigerant gas is sent to the compressor. ing. This is to prevent the compressor from sucking the liquid refrigerant and causing the liquid compression to cause a valve failure or the like to shorten the life of the compressor.

Here, the compressor is stopped when the cooling / heating operation is not performed, and when the stop time is long, the outdoor unit including the compressor changes at a temperature almost equal to the outside air temperature. When the outside air temperature is low, the refrigerant liquefies, and the liquid refrigerant accumulates inside the accumulator or the compressor, and liquid compression occurs when the compressor is started.

As a countermeasure against this, conventionally, a compressor is provided with a heater, the heater is heated to raise the temperature of the compressor to a predetermined temperature or higher, and the compressor in the compressor is vaporized and then started. Are known.

[0005]

However, when the indoor heat exchanger and the outdoor heat exchanger are installed separately from each other, the amount of the charged refrigerant increases, and the heat exchanger may be left for a long time at a low outdoor temperature. As the liquefaction of the refrigerant progresses, the liquid refrigerant overflows from the accumulator and flows into the compressor, or the compressor sucks the liquid refrigerant from the accumulator, and the compressor causes liquid compression when the compressor is started with only the heater described above. This problem could not be prevented, and measures such as increasing the size of the accumulator were required.

The present invention has been made in view of the above-mentioned problems, and has been made in consideration of the above-described problems. A heat pump air conditioner capable of preventing liquid compression even at a low outside air temperature or when a compressor is started after being left for a long time without increasing the size of an accumulator. It is intended to provide a device.

[0007]

According to the first aspect of the present invention, there is provided an accumulator (1).
0) part or compressor (2) and accumulator (10)
And an evaporating means (30) for gasifying the liquid refrigerant is provided in the suction-side refrigerant passage (20).

As a result, the liquid refrigerant is gasified in the accumulator or immediately before being sucked into the compressor.
Liquid compression at the time of starting the compressor can be prevented without increasing the size of the accumulator.

According to the second aspect of the present invention, the accumulator heating means (12) for heating the refrigerant is provided in the accumulator (10) as the evaporation promoting means (30), and the accumulator (10) and the receiver (6) are provided. And a liquid refrigerant circuit (13) communicating with the control device (4).
00) controls the operation of the accumulator heating means (12) and the liquid refrigerant circuit (13) according to the state of the liquid refrigerant in the accumulator (10), and
The refrigerant in the accumulator (10) is heated by heating the refrigerant in the liquid refrigerant circuit (0), and a part of the liquid refrigerant in the accumulator (10) is removed by the pressure increase.
And moving it to the receiver (6) via the.

[0010] Thus, the liquid level of the liquid refrigerant in the accumulator can be lowered, and it is possible to prevent the liquid refrigerant from being sucked when the compressor is started and causing liquid compression.

According to the third aspect of the present invention, the control device (4
00) is the outside air temperature (To) which is the environment of the outdoor unit (300) including the compressor (2) and the accumulator (10).
Is lower than the set temperature (to) or the compressor (2)
When the stop time (H) of the heat pump type air conditioner (100) including the above is longer than the set time (h), the compressor (2)
Before starting, the heating by the accumulator heating means (12) is performed.

[0012] Thus, the compressor which lowers the liquid level of the liquid refrigerant in the accumulator only at a low outside air temperature or when the refrigerant is left for a long period of time, especially when the liquefaction of the refrigerant proceeds and liquid compression easily occurs. Activation will be performed.

According to a fourth aspect of the present invention, the accumulator heating means (12) utilizes cooling water of the engine (1).

[0014] Thus, by passing the cooling water of the engine through the accumulator during the warm-up operation, the refrigerant can be heated at the same time, and an energy-saving heating means utilizing the exhaust heat of the engine can be provided.

According to a fifth aspect of the present invention, an electric heater (17) is used for the accumulator heating means (12).

Although this requires electric energy as compared with the use of cooling water for the engine, it can be constructed relatively simply by winding an electric heater around an accumulator as heating means.

In the invention according to claim 6, the compressor (2)
Compressor heating means (18a, 18b) for heating
The control device (400) includes an accumulator heating means (1
2) and the compressor heating means (18a, 18b) are controlled to heat the refrigerant in the accumulator (10) and the compressor (2).

Thus, the portion where the liquid refrigerant accumulates and tends to cause liquid compression is simultaneously heated and controlled to prevent liquid compression.

According to a seventh aspect of the invention, the cooling water of the engine (1) is used for the compressor heating means (18a, 18b).

Thus, even for a compressor which has been conventionally heated by an electric heater, it becomes an energy-saving heating means utilizing exhaust heat by passing the cooling water of the engine through the outer surface, and is combined with the heating means of the accumulator. The configuration and control can reduce costs.

According to the present invention, as the evaporation promoting means (30), the compressor (2) and the accumulator (1) are used.
0), the compressor (2)
And a pressure reducing unit (24) for reducing the pressure of the refrigerant supplied to the cooling unit.

Accordingly, the refrigerant sucked into the compressor is:
When the pressure is reduced in the decompression section, the evaporation is promoted to become a gaseous refrigerant, and liquid compression can be prevented.

According to the ninth aspect of the present invention, as the evaporation promoting means (30), the compressor (2) and the accumulator (1) are used.
0) between the suction side refrigerant passage (20) and the opening / closing means (2).
5) is provided, and the control device (400) drives the opening / closing means (25) simultaneously with the start of operation of the compressor (2), and sets a predetermined time (T) from the fully closed to the fully opened suction side refrigerant passage (20). It is characterized by being opened over.

[0024] Thus, immediately after the start of the compressor in which liquid compression is likely to occur, the suction side refrigerant passage is narrowed by the opening / closing means, and the pressure of the compressor side becomes lower than that of the accumulator side, so that the refrigerant passing through the opening / closing means is reduced. Evaporation is promoted by the pressure drop and the refrigerant becomes a gaseous refrigerant, so that liquid compression can be prevented. In addition, the opening / closing means gradually weakens the throttle to be fully opened, and a steady operation is performed.

The reference numerals in parentheses attached to the respective means indicate the correspondence with specific means described in the embodiments described later.

[0026]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings.

(First Embodiment) FIG. 1 is a schematic configuration diagram schematically showing a configuration of a heat pump air conditioner 100 according to a first embodiment of the present invention. The present embodiment is driven by a water-cooled engine (for example, a diesel engine) 1, and the heat pump air conditioner 100 is used as a stationary or vehicle-mounted air conditioner.
Although it is possible to cool and heat the room or the cabin, this embodiment will be described as applied to a stationary type.

The heat pump cycle 200 (portion surrounded by a two-dot chain line in FIG. 1) is configured by connecting the respective functional members with refrigerant pipes. During indoor heating, the compressor 2 → the four-way valve 3 →
Indoor heat exchanger 4 → indoor unit electric valve 5 → receiver 6 → outdoor unit electric valve 7 → outdoor heat exchanger 8 → four-way valve 3 → refrigerant heater 9 →
The refrigerant is circulated in the order of the accumulator 10 and the compressor 2 (solid arrows) to heat the refrigerant.

During indoor cooling, the compressor 2 → the four-way valve 3 → the outdoor heat exchanger 8 → the outdoor unit electric valve 7 → the receiver 6 → the indoor unit electric valve 5 → the indoor heat exchanger 4 → the four-way valve 3 → the refrigerant heating The refrigerant is circulated (dashed arrow) in the order of the heat exchanger 9 → the accumulator 10 → the compressor 2 for cooling.

The indoor heat exchanger 4 functions as a first heat exchanger as a condenser during heating, and functions as a second heat exchanger as an evaporator during cooling. In addition, the outdoor heat exchanger 8
Functions as a second heat exchanger that is an evaporator during heating, and functions as a first heat exchanger that is a condenser during cooling.

During heating, the outdoor unit electric valve 7 functions as an expansion valve as a pressure reducing means for reducing the pressure of the refrigerant, and during cooling, the indoor unit electric valve 5 functions as an expansion valve as a pressure reducing means.

The engine 1 transmits a driving force to a pulley 2a provided on the compressor 2 by a V-belt 1b wound around a crank pulley 1a. An electromagnetic clutch 2b is provided between the pulley 2a and the compressor 2 as driving force switching means for transmitting or blocking the driving force transmitted to the pulley 2a to the compressor 2.

The compressor 2 has a built-in electric heater for vaporizing a conventional liquid refrigerant. The refrigerant pipe 21 connected to the discharge side (the four-way valve 3 side) of the compressor 2 is provided with a well-known oil separator 22 that separates oil from the refrigerant discharged by the compressor 2. The oil separated by the oil return tube 23
Through the suction side of the compressor 2 (accumulator 10
The pressure is returned by the differential pressure across the compressor 2 into the path of the refrigerant pipe 20 connected to the side (side).

Numeral 11 denotes a cooling water circuit, which is formed in the main body of the engine 1 and has a cooling water passage (not shown) for cooling the engine 1. Water switching valve 113, cooling water pump 1
14, a first cooling water circuit 111 returning to the cooling water passage inlet, and a radiator 11 from the cooling water passage outlet.
5, a cooling water switching valve 113, and a second cooling water circuit 112 which sequentially flows through the cooling water pump 114 and returns to the cooling water passage inlet.

Here, the cooling water pump 114 is an electric pump, and the cooling water switching valve 113 is an electromagnetic switching valve for switching between the first cooling water circuit 111 and the second cooling water circuit 112. The radiator 115 is a well-known heat exchanger for exchanging heat between the cooling water and the outside air. The refrigerant heater 9 is a double-pipe heat exchanger made of, for example, metal and the like. It is exchangeable. The entrance and exit of the cooling water passage and the members 9, 113 to 115 are connected by, for example, a rubber hose or the like.

As a new configuration of the present invention, the cooling water passage 11 branches off from the cooling water passage outlet, passes through the accumulator 10 as the accumulator heating means 12, flows through the cooling water pump 114, and passes through the cooling water passage 114. A cooling water circuit 13 returning to the inlet is formed, and is opened and closed by an electromagnetic valve 14. Further, a liquid refrigerant circuit 15 communicating from the bottom of the accumulator 10 to the upper part of the receiver 6 is configured, and is opened and closed by an electromagnetic valve 16.

In the heat pump type air conditioner 100 having the above configuration, the indoor heat exchanger 4 and the indoor unit electric valve 5 among the constituent elements constitute an indoor unit and are installed at appropriate places in the room. The outdoor unit 300 (a portion surrounded by a dashed line in FIG. 1) is configured and installed at an appropriate location outside the room. The heat pump air conditioner 100 has a control device 400 as control means including an electronic circuit. The control device 400 includes a controller provided in a room (not shown), an outside air temperature sensor, a refrigerant temperature sensor (not shown),
Information from a water temperature sensor or the like is input, and the operation of the indoor unit and the outdoor unit 300 is controlled.

Next, the operation of this embodiment will be described based on the above configuration.

When power is supplied to the heat pump type air conditioner 100, the control device 400 executes either control processing during heating operation or control processing during cooling operation based on information from a controller (not shown). I do.

First, the operation during the heating operation will be described. For example, when the outside air temperature is low, a heating switch of a controller (not shown) is turned on, and when an ON signal is input to the control device 400, the control device 400 executes a control process during a heating operation. The control device 400 switches the four-way valve 3 to the heating side (solid line), starts the engine 1 and drives the compressor 2. In addition, the indoor unit electric valve 5 is fully opened, and the outdoor unit electric valve 7 is adjusted to an opening degree that functions as an expansion valve.

The high-temperature gas refrigerant that has exited the compressor 2 is first subjected to oil separation by an oil separator 22. The separated oil is supplied to the refrigerant pipe 2 via an oil return tube 23 by a pressure difference between the refrigerant pipe 20 and the refrigerant pipe 21.
Sent to 0. The refrigerant that has exited the oil separator 22 passes through the four-way valve 3, is condensed in the indoor heat exchanger 4, heats, is separated into gas and liquid by the receiver 6, is decompressed by the electric valve 7 of the outdoor unit, and is decompressed by the outdoor heat exchanger 7. After evaporating at 8 and passing through the four-way valve 3 again, the refrigerant is heated by the heat exchange with the cooling water from which the engine exhaust heat has been recovered by the refrigerant heater 9, and then returns to the compressor 2 from the accumulator 10.

When the engine 1 is started, the cooling water pump 114 is also started, and the cooling water switching valve 113 is switched so that the cooling water flows to the first cooling water circuit 111. The cooling water pumped by the cooling water pump 114 flows through the cooling water passage in the engine 1, absorbs the exhaust heat of the engine, enters the refrigerant heater 9, where the refrigerant evaporated in the outdoor heat exchanger 8 and The refrigerant is heated by heat exchange. After that, the cooling water switching valve 113 returns to the cooling water pump 114, and is sent again to the cooling water passage in the engine 1.

Since the cooling water circulates in this way, the exhaust heat of the engine 1 is recovered by the cooling water, and is used for heating the refrigerant by the refrigerant heater 9 and becomes a part of the heating heat source of the heat pump cycle 200. .

Next, the operation during the cooling operation will be described. For example, when the outside air temperature is high, a cooling switch of a controller (not shown) is turned on, and when an ON signal is input to the control device 400, the control device 400 executes control processing during cooling operation. The control device 400 switches the four-way valve 3 to the cooling side (broken line), starts the engine 1 and drives the compressor 2. In addition, the outdoor unit electric valve 7 is fully opened, and the indoor unit electric valve 5 is adjusted to an opening degree that functions as an expansion valve.

The high-temperature gas refrigerant that has left the compressor 2 is first subjected to oil separation by an oil separator 22. The separated oil is supplied to the refrigerant pipe 2 via an oil return tube 23 by a pressure difference between the refrigerant pipe 20 and the refrigerant pipe 21.
Sent to 0. The refrigerant flowing out of the oil separator 22 passes through the four-way valve 3, is condensed in the outdoor heat exchanger 8, is separated into gas and liquid by the receiver 6, is decompressed by the indoor unit electric valve 5, and is decompressed by the outdoor heat exchanger 8.
After evaporating and performing cooling, the refrigerant passes through the four-way valve 3 again, and is subsequently sent from the refrigerant heater 9 to the accumulator 10,
The gas-liquid separation is performed by the accumulator 10 and the process returns to the compressor 2.

When the engine 1 is started, the cooling water pump 114 is also started, and the cooling water switching valve 113 is switched so that the cooling water flows to the second cooling water circuit 112. The cooling water pumped by the cooling water pump 114 flows through the cooling water passage in the engine 1, absorbs the exhaust heat of the engine, and then enters the radiator 115. Then, the cooling water switching valve 1
From 13, it returns to the cooling water pump 114 and is sent again to the cooling water passage in the engine 1. Since the cooling water circulates in this manner, the exhaust heat of the engine 1 is recovered by the cooling water, and the radiator 115 exchanges heat with the outside air to radiate heat.

Next, the control operation of the control device 400 when the apparatus is started will be described with reference to the flowchart shown in FIG.

A switch of a controller (not shown) is turned on.
Then, when an ON signal is input to the control device 400, the control device 400 executes a control process at the time of startup. First, as step S1, the engine 1 is started and the cooling water pump 114 is also started.

Next, in step S2, it is determined whether the stop period of the heat pump air conditioner 100 is not long.
It is determined whether or not the stop time H counted from the previous time when the use of the air conditioner 100 is stopped by the integration timer in 00 does not exceed the set time h. If it exceeds, the operation of step S4 described below is performed, and if it does not exceed, the process proceeds to the next step S3.

In step S3, the outside air temperature To is detected by an outside air temperature sensor (not shown) to determine whether the environmental temperature of the outdoor unit 300 including the compressor 2 and the accumulator 10 is low.
Is lower than the set temperature to. If it is lower, the operation of step S4 described below is performed, and if it is not lower, the operation of step S7 described later is performed.

If it is determined that the halt period H of the air conditioner 100 is long or the environmental temperature To is low, first, at step S4, the electric heater built in the compressor 2 is turned on and the cooling water circuit 13 is turned on. The solenoid valve 14 and the solenoid valve 16 of the liquid refrigerant circuit 15 are opened. As a result, the liquid refrigerant in the compressor 2 is vaporized, and the liquid refrigerant in the accumulator 10 is heated by the cooling water of the engine to promote evaporation, and the pressure increase causes the liquid refrigerant in the accumulator 10 to turn into a liquid refrigerant circuit. It moves from 15 to the receiver 6.

Next, in step S5, it is determined whether the cooling water temperature of the engine 1 has risen sufficiently based on a water temperature Tw detected by a water temperature sensor (not shown) of 40 ° C. or higher. If it has exceeded, in step S6, the electric heater built in the compressor 2 is turned off, and the solenoid valve 14 of the cooling water circuit 13 is turned off.
Then, the electromagnetic valve 16 of the liquid refrigerant circuit 15 is closed. And
In step S7, the compression of the refrigerant is started by turning on the electromagnetic clutch 2b of the compressor 2, and the heat pump cycle is started.

With the above-described structure and operation, the liquid refrigerant in the accumulator 10 is heated to promote the evaporation only at a low outside temperature where the refrigerant is liquefied and the liquid compression is likely to occur, or only under the condition after leaving for a long time. Then, the compressor 2 is started after lowering the liquid level of the liquid refrigerant in the accumulator 10 due to the increase in the pressure, and it is possible to prevent the liquid refrigerant from being sucked in at the time of starting and causing liquid compression.

Further, by passing the cooling water of the engine 1 during the warm-up operation through the accumulator 10, the above-described heating of the refrigerant can be performed at the same time, and an energy-saving heating means utilizing the exhaust heat of the engine can be provided.

FIG. 3 is a schematic configuration diagram when an electric heater 17 is used as the accumulator heating means 12.
As a result, electric energy is required as compared with the use of the cooling water of the engine 1.
2 can be relatively simply constructed by winding the electric heater 17 around the accumulator 10, and the energization control may be performed together with the electric heater of the conventional compressor 2. Therefore, when the present invention is applied to the existing device 100, Easy.

FIG. 4 shows that the heating means of the compressor 2 has the engine 1
FIG. 3 is a schematic configuration diagram when cooling water is used, and FIG. 4A shows a double jacket structure 18a around the compressor 2;
In the meantime, the heating is performed by passing the cooling water from the cooling water circuit 13, and (b) is obtained by circulating the cooling water pipe 18 b around the compressor 2 and heating the cooling water from the cooling water circuit 13 there. .

As a result, the cooling water of the engine 1 is passed through the outer surface of the compressor 2 which has been conventionally heated by an electric heater. By configuring and controlling in conjunction with, the cost can also be reduced.

(Second Embodiment) FIG. 5 is a schematic configuration diagram schematically showing the configuration of a heat pump air conditioner 100 according to a second embodiment of the present invention. The difference from the first embodiment of FIG. 1 lies in that the compressor 2 and the accumulator 1 are replaced with the absence of the accumulator heating means 12 and the liquid refrigerant circuit 15.
An expansion tank 24 is provided as a decompression unit in the suction-side refrigerant passage 20 between 0 and 0.

As a result, the refrigerant sucked into the compressor 2 is reduced in pressure in the expansion tank 24 to promote evaporation and becomes a gaseous refrigerant, thereby preventing liquid compression.

Also, there is an effect that the liquid refrigerant sucked from the accumulator 10 is trapped in the expansion tank 24 and is not flown to the compressor 2. The refrigerant temporarily stored in the expansion tank 24 evaporates during the steady operation.

(Third Embodiment) FIG. 6 is a schematic configuration diagram between a compressor 2 and an accumulator 10 according to a third embodiment of the present invention. The premise of the heat pump air conditioner 100 is the same as that of the second embodiment shown in FIG. 5 except that an electric valve 25 as an opening / closing means is provided in the suction side refrigerant passage 20 instead of the expansion tank 24. ing.

In operation, an air conditioner switch of a controller (not shown) is turned on, and an ON signal is sent to the controller 400.
, The control device 400 starts the cooling or heating operation control process. Then, as shown in FIG. 7, at the same time that a signal for starting the operation of the compressor 2 is output from the control device 400, the electric valve 25 is driven, and a predetermined time (T) is required from the fully closed to the fully opened suction side refrigerant passage 20. I tried to open it.

Thus, the compressor 2 in which liquid compression is likely to occur
Immediately after the start of the operation, the suction side refrigerant passage 20 is throttled by the electric valve 25, the compressor 2 side has a low pressure with respect to the accumulator 10 side, and the refrigerant passing through the electric valve 25 is promoted to evaporate due to the pressure drop. Liquid compression can be prevented by being a gaseous refrigerant. In addition, the electric valve 25 gradually weakens the throttle and becomes fully open, so that a steady operation is performed.

FIG. 8 shows a configuration in which a plurality of solenoid valves 26 are provided in parallel as opening / closing means for restricting the suction-side refrigerant passage 20. These solenoid valves 25 are sequentially opened simultaneously with the start of operation of the compressor 2. It may be. Although the electric valve 25 is continuously opened, the difference is that it is opened step by step, but the same effect can be obtained.

In the above embodiment, the engine 1 is a diesel engine. However, the invention is not limited to this, and may be a gasoline engine, a gas engine, or the like.

In the above embodiment, the compressor 2 is driven by the engine 1. However, the compressor 2 may be driven by an electric compressor or the like other than the engine.

The present invention may be applied not only to a heat pump cycle but also to other refrigerant compression refrigeration cycles.

[Brief description of the drawings]

FIG. 1 is a schematic configuration diagram schematically showing a configuration of a heat pump air conditioner 100 according to a first embodiment of the present invention.

FIG. 2 is a flowchart showing a control operation at the time of starting the apparatus.

FIG. 3 is a schematic configuration diagram when an electric heater is used as a heating unit of the accumulator.

FIG. 4 is a schematic configuration diagram when cooling water of an engine is used for heating means of a compressor.

FIG. 5 is a schematic configuration diagram schematically illustrating a configuration of a heat pump air conditioner 100 according to a second embodiment of the present invention.

FIG. 6 is a schematic configuration diagram between a compressor and an accumulator according to a third embodiment of the present invention.

FIG. 7 is a sequence diagram showing an opening and closing operation of a motor-operated valve.

FIG. 8 is a schematic configuration diagram when a plurality of solenoid valves are used.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Engine 2 Compressor 4 Indoor heat exchanger (1st heat exchanger at the time of heating, 2nd heat exchanger at the time of cooling) 5 Indoor unit electric valve (decompression means at the time of cooling) 6 Receiver 7 Outdoor unit electric valve (heating) 8) Outdoor heat exchanger (first heat exchanger during cooling, second heat exchanger during heating) 10 Accumulator 12 Accumulator heating means 15 Liquid refrigerant circuit 17 Electric heater (Accumulator heating means) 18a, 18b Compressor heating means 20 Refrigerant pipe (suction side refrigerant passage) 24 Expansion tank (decompression unit) 25 Electric valve, solenoid valve (Opening / closing means) 30 Evaporation promoting means 100 Heat pump air conditioner 300 Outdoor unit 400 Control device H Stop time h Setting Time T Predetermined time To Outside air (environment) temperature to Set temperature

Claims (9)

[Claims] 1. A compressor (2) for compressing a refrigerant, first heat exchangers (4, 8) for exchanging heat between the refrigerant and air to cool the refrigerant, and decompression means for decompressing the refrigerant. (5,
7), a second heat exchanger (4, 8) for exchanging heat between the refrigerant and air to heat the refrigerant, a receiver (6) for storing the refrigerant in gas-liquid separation, and an accumulator (10). A heat pump cycle air-conditioning apparatus comprising: a heat pump cycle formed by connecting the heat pump cycle by a refrigerant pipe; and a control device (400) for controlling the heat pump cycle. The accumulator (10) section or the compressor (2) A heat pump type air conditioner, wherein an evaporation promoting means (30) for gasifying a liquid refrigerant is provided in a suction side refrigerant passage (20) between the accumulator (10) and the accumulator (10). 2. An accumulator heating means (12) for heating the refrigerant in the accumulator (10) as the evaporation promoting means (30), and the accumulator (10) communicates with the receiver (6). And a liquid refrigerant circuit (13).
00) controls the operation of the accumulator heating means (12) and the liquid refrigerant circuit (13) according to the state of the liquid refrigerant in the accumulator (10), and heats the refrigerant in the accumulator (10). The pressure rise causes a part of the liquid refrigerant in the accumulator (10) to move to the receiver (6) via the liquid refrigerant circuit (13). Heat pump air conditioner. 3. The control device (400), wherein an outside air temperature (To) as an environment of an outdoor unit (300) including the compressor (2) and the accumulator (10) is lower than a set temperature (to). In the case, or when the stop time (H) of the heat pump air conditioner (100) including the compressor (2) is longer than the set time (h), the accumulator heating is performed before the compressor (2) is started. The heat pump type air conditioner according to claim 1 or 2, wherein heating is performed by the means (12). 4. The accumulator heating means (12)
The heat pump type air conditioner according to any one of claims 1 to 3, wherein cooling water of the engine (1) is used. 5. The accumulator heating means (12).
The heat pump type air conditioner according to any one of claims 1 to 3, wherein an electric heater (17) is used. 6. Compressor heating means (18a, 18b) for heating said compressor (2) is provided, and said controller (40)
0) controls the accumulator heating means (12) and the compressor heating means (18a, 18b) to heat the refrigerant in the accumulator (10) and the compressor (2). The heat pump type air conditioner according to any one of claims 1 to 5. 7. The compressor heating means (18a, 18b)
The heat pump air conditioner according to claim 6, wherein cooling water of the engine (1) is used. 8. A refrigerant to be supplied to the compressor (2) as the evaporation promoting means (30) through a suction-side refrigerant passage (20) between the compressor (2) and the accumulator (10). The heat pump air conditioner according to claim 1, further comprising a pressure reducing unit (24) for reducing the pressure. 9. An opening / closing means (25) is provided in the suction side refrigerant passage (20) between the compressor (2) and the accumulator (10) as the evaporation promoting means (30), and the control device ( 400) drives the opening / closing means (25) simultaneously with the start of operation of the compressor (2), and opens the suction-side refrigerant passage (20) from fully closed to fully open for a predetermined time (T). The heat pump type air conditioner according to claim 1, wherein: