JPS5966663A - Heat pump type heating apparatus - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a heat pump type heating device, and more particularly to a heat pump type heating device, which is equipped with a gas-liquid separator, and compresses a gas refrigerant from an evaporator and an intermediate-pressure gas refrigerant separated by the gas-liquid separator using a compressor. Regarding what you choose to do.

Conventionally, as one of such heat pump 7 heating YFR devices 6, there is an intermediate pressure gas injection type. As shown in Fig. 1, this device includes a compressor (a),
An indoor heat exchanger (b) as a condenser, an expansion mechanism (C), (d-) consisting of a capillary tube, etc., and a gas-liquid separator disposed between the expansion mechanism (C) (a) (e) and an outdoor heat exchanger (f) as an evaporator, and after condensing the gas refrigerant discharged from the compressor discharge boat (aΦ) in the outdoor heat exchanger (b), an expansion mechanism (C), d), the gas-liquid separator (8) separates the gas refrigerant into a gas refrigerant and a liquid refrigerant, and the intermediate-pressure gas refrigerant is transferred to an injection boat (aJ-Liquid) during the compression stroke of the compressor (a). /Jection''!4Meanwhile, after the liquid refrigerant is evaporated in the outdoor heat exchanger (f), it is introduced into the suction port ia of the compressor (a), and the compressor (a) By repeating the cycle of compressing the gas refrigerant together with the pressure gas refrigerant, the heating capacity is improved by increasing the amount of refrigerant circulated by the intermediate pressure gas refrigerant.
112,52)).

4. As the compressor (a), a rolling piston type compressor is usually used. The rolling piston compressor has a cylindrical cylinder (a) as shown in FIG.
4), a rotor (aρ) that rotates eccentrically while inscribed in the cylinder (a), and a rotor (aρ) that is partially recessed on the inner circumferential surface of the cylinder (a611) and a rotor (a) that is pressed against the rotor (a611). The above-mentioned opening is provided with a bay (a,) that is in constant sliding contact with the outer circumferential surface of the cylinder, and a suction boat (a) and a discharge boat ( a, ll, and the above-mentioned cylinder (injection port opened on the side wall of aρ) (aJ).As the rotor (s) rotates, the cylinder (aρ) and the rotor (
The working chamber (aρ,
(By opening and closing one side of the injection port on the side wall of the rotor), after inhaling the girth refrigerant from the suction boat
Injection boat 1. 71. It has a pressure of 7.4 yen, 6 yen and 7.4 yen, and is made to compress and discharge from the discharge port (Japanese Patent Laid-Open No. 54-6162
(see publication).

However, in the conventional method described above, 1. The intermediate-pressure gas refrigerant flows back to the outdoor heat exchanger (f) through the working chamber (la & la capacity port) immediately before the compression stroke, and the compressed gas refrigerant at a pressure higher than that of the intermediate-pressure gas refrigerant is compressed. In order to prevent backflow to the gas-liquid separator (θ) through the working chamber (a) and the injection valve at the end of the stroke, the injection port (a) has a limited opening period.
As a result, the optimal amount of intermediate-pressure gas refrigerant could not be injected under all load conditions, and there was a problem that there was a limit to the improvement of heating capacity and the purpose of the hyperactive refrigeration cycle could not be fully achieved. .

Therefore, if the gas refrigerant from the outdoor heat exchanger (f) (evaporator) and the intermediate pressure gas refrigerant from the gas-liquid separator (e) are compressed separately using separate compressors, the intermediate pressure Although it is possible to inject the entire optimal amount of gas refrigerant, a separate compressor is required, which increases costs and causes problems such as an increase in storage volume.

In addition, the intermediate pressure gas refrigerant is injected from the time when the gas pressure in the working chamber (Q is lower than the intermediate pressure) to the intermediate pressure. After the pressure drops to the following pressure, it is compressed again to an intermediate pressure, so the loss due to this compression work is lost, and the EER improvement due to injection operation is 4~
The drawback was that it was only around 5 inches.

On the other hand, as a simple two-stage compression type that performs intermediate pressure gas injection,
As disclosed in Japanese Patent No. 0, a rotor and two vanes 1. A high-stage compression chamber and a high-stage compression chamber are defined, each compression chamber is provided with a suction boat and a discharge port, and the low-stage discharge boat is connected to the high-stage suction boat. A rolling piston compressor has been proposed that achieves cost reduction and compactness by integrating the compressor by performing staged compression.

In view of this, the present invention was made by focusing on the use of a rolling piston type or sliding vane type compressor having a plurality of compression chambers as described above in an intermediate pressure gas injection type heat pump type heating device. By compressing the intermediate-pressure gas refrigerant from the gas-liquid separator and the gas refrigerant from the evaporator in separate compression chambers in one compressor, costs increase and storage capacity increases. The optimum amount of refrigerant is drawn into the compressor by prolonging the period during which intermediate-pressure gas refrigerant is drawn into the compressor at intermediate pressure.□
To increase heating capacity and eliminate compression work loss by directly compressing intermediate pressure gas refrigerant from intermediate pressure to discharge pressure, thereby greatly improving Ell, E, and R. The purpose is to

To achieve this objective, the configuration of the invention comprises a mouth-ring piston type or sliding vane type compressor;
It comprises a condenser, two or more expansion mechanisms, one or more gas-liquid separators disposed at respective intermediate portions of the expansion mechanisms, and an evaporator, the gas refrigerant from the evaporators and A heat pump heating device in which the intermediate pressure gas refrigerant separated by the gas-liquid separator is compressed by the compressor,
A plurality of vanes arranged in the cylinder of the compressor define a space between the cylinder and the rotor into a main compression chamber and one or more sub compression chambers each having a suction boat, a discharge boat, and a metal. , the suction boat of the main compression chamber is connected to the evaporator, the suction boats of the sub compression chambers are each connected to the corresponding gas-liquid separators, and the discharge boats of the main and sub compression chambers are assembled. This is connected to the condenser, thereby compressing the gas refrigerant from the evaporator to a predetermined discharge pressure in the main compression chamber, while compressing the intermediate pressure gas refrigerant from the gas-liquid separator to the same predetermined discharge pressure in the sub-compression chamber. It is 1- so that it can be compressed into .

Embodiments of the present invention will be described in detail below with reference to the drawings.

Figure 2 shows a first embodiment in which the present invention is applied to a heat pump type heating system, in which (1) a d-ring piston type compressor, (2) a four-way switching valve, and (3) a heating system. Indoor heat exchanger that functions as a condenser during operation and as an evaporator during cooling operation; Machine groove, +7L (8id, expansion 1 i'i4 [4)
+ High-pressure side and low-pressure side gas-liquid separators are installed in each middle of (5) + +6)...6, and (9) functions as an evaporator during heating operation, and functions as a condenser during cooling operation. These are outdoor heat exchangers, and are connected to each other by communication pipes (10) to (19) as refrigerant passages.

In addition, e2[11, I'21)rIi each above k
Connect the gas section of the 7 & minute 1'fI device (7], +8) to the suction bow 1- (2'7a), (2f3a) of the sub compression chamber (27), U8) of the compressor tl+, which will be described later. Gas/f nozzle tube, (20a), (
21a) ID each gas injector tube (2o), (
21), each of which is a solenoid valve that is installed in the middle of the air conditioner and opens during heating operation.

The rolling piston type compressor (1) has a cylindrical cylinder (22), an 0-taper (z3) which is inscribed in the cylinder (22) and rotates eccentrically, and which can freely protrude and retract from the inner peripheral surface of the cylinder (22). Nikatsu Spring (24+, (24L (
24), and is provided with three vanes (25) + 12$ + (25) that are pressed against the rotor (2,'3) side and are always in sliding contact with the outer peripheral surface of the rotor (23), and each vane 125 ) + (25) + j25) From K, the space between the cylinder (4) and the rotor (23) is the main compression chamber (26) and the two sub compressors 1 on the high pressure side and low ratio side.
27) and (28). Furthermore,”−
The blending compression chamber f26), fd in (27L 128), and the suction boat (26) which opens on the inner peripheral surface of the cylinder (22).
a,), (2'7a,).

(28a), discharge boat (26b), (2'7b
), (28b) and each discharge board) (26b
), (27b), (28b) are connected to each compression chamber (26), (27b) from the cylinder (22) outside) 11S.
), (28) prevents the backflow of gas refrigerant to 1-. Sliding valves (26c), (2'7c), and (28c) are installed. The suction bow (26a) of the main compression chamber (26) is connected to the evaporator (indoor heat exchanger (during cooling operation)
3) or an outdoor heat exchanger (9)) during heating operation, while the suction boats (27a) and (28a) of each sub-compressor (27) and si8) are connected to gas injection pipes (2o ).

Gas-liquid separator +7L (8+
It is connected to the. ¥1: The above main and sub compression chamber 12fi).

t27L 128+ each discharge bow) (26b), (2
7b) and (28b) are the collection pipe (29), respectively.
(13 [f), connecting pipe (10) via +31+
The condenser (indoor heat exchanger during heating operation (3)
Alternatively, it is connected to the outdoor heat exchanger (9) during cooling operation.

Therefore, during heating and cooling operation, as the rotor (23) rotates in the direction of the dashed arrow, each compression chamber I213)1t27)
, +28) to expand the compression chamber (26+, t27).
L (28+ each suction boat (26a), (2″7a)
), (28a) to the evaporator (the indoor heat exchanger (3) during cooling operation is also connected to the outdoor heat exchanger (9) during heating operation)
) and the intermediate-pressure gas refrigerant separated by the gas-liquid separator +7) and (8), respectively.
G)・(27), 12N-contraction I7 and each compression chamber 12
[3), (27), (, 28) gas refrigerant is compressed and discharged from the boat (26b), (27b), (28b)
It is configured to discharge from (compression stroke).

Next, to explain the operation of the first embodiment, during heating operation, the four-way switching valve (2) is switched as shown by the solid line to allow the refrigerant to flow as shown by the arrow, and the outdoor heat exchanger (9) (evaporation The low-temperature gas refrigerant from the main compression chamber (26) is sucked into the main compression chamber (2G) from the suction port (26a) of the main compression chamber (26), and then compressed to a predetermined pressure in the main compression chamber (26) and sent to the discharge port. (26b). On the other hand, high pressure '+uu
The intermediate pressure gas refrigerant from the gas-liquid separator (7) and the low-pressure side gas-liquid separator (8) is transferred to the corresponding high-pressure side and low-pressure side sub-compression chambers (2'7) and throat suction ports (2'7), respectively. ”a)
(2Eia) After the intermediate pressure is sucked into each sub-compression chamber (27), the pressure is approximately the same as the discharge pressure of the main pressure chamber (2G). It is compressed in a trench and discharged into a boat' (27b).

(2'81)). Then each discharge boat (26b).

(2'71)), (28b) is collected in the communication pipe (10), and the indoor heat exchanger (
3) It is cooled and liquefied in the (condenser), and the first expansion mechanism (4)
The refrigerant is expanded and sent to the high-pressure side gas-liquid separator (7), where it is separated into an intermediate-pressure gas refrigerant set at a high pressure and a liquid refrigerant.

The intermediate pressure gas refrigerant is then placed in the high pressure side sub compression chamber (27).
While the liquid refrigerant is sucked into the second expansion mechanism (5
) and sent to the low-pressure gas-liquid separator (8), where it is separated into an intermediate-pressure gas refrigerant set at a low pressure and a liquid refrigerant. Gas refrigerant is □
Low pressure side sub compression chamber (while intermediate pressure is sucked into 2si,
The liquid refrigerant is further expanded by the third expansion mechanism (6) and sent to the outdoor heat exchanger (9).
Heating operation is performed by increasing the amount of refrigerant circulation through two-stage suction and compression of intermediate-pressure gas refrigerant that is vaporized in the evaporator.

On the other hand, during J cooling operation, the four-way selector valve (2) is switched as shown by the broken line to flow the refrigerant in the opposite direction to that during heating operation, thereby performing cooling operation.

Therefore, during heating operation, the intermediate pressure gas refrigerant is sucked in and compressed in two stages by the high pressure side and the low pressure side, so the amount of refrigerant circulation can be increased and the heating capacity can be improved.

Moreover, the high-pressure side and low-pressure side gas-liquid separators [7], (8
), the intermediate pressure gas refrigerant from each outdoor heat exchanger (9
) (steamer) (steamer) (main compression chamber for compressing low-temperature gas refrigerant from the steamer) (high-pressure side and low-pressure side sub-compression chambers (27) for intermediate-pressure gas refrigerant, which are provided separately from the 2-gas refrigerant, intermediate-pressure suction in ρ) Each sub-compression chamber (2 forces) is compressed.

There is no need to consider the opening position of the suction port (stirrup 2L), (28a), which reduces restrictions and allows the suction period of the intermediate pressure gas refrigerant to be set longer.As a result, the intermediate pressure gas refrigerant The optimal amount can be inhaled under the load conditions, which further enhances the injection effect.Therefore, the heating capacity can be greatly improved, and the ability of the hyperactive refrigeration cycle can be fully demonstrated. .

In addition, the intermediate pressure gas refrigerant from each blood separator (7), (81) is maintained at an intermediate pressure approximately corresponding to the time of inhalation in each sub compression chamber (27), which is separate from the main compression chamber (26).
j.

h8) Since m occurs when inhaling intermediate pressure, the pressure when inhaling intermediate pressure □
There is no drop, and compression can be performed from intermediate pressure to discharge pressure directly after suction.Therefore, there is no compression work loss, and compression efficiency can be increased, increasing HEH by injection operation f: about 8 to 10%. be able to.

In addition, since the gas refrigerant from the evaporator and each gas-liquid separator (7) are used to compress the intermediate-pressure gas refrigerant from 81 (1 compressor + 1), it is not necessary to use separate compressors. It is possible to achieve compactness.

In addition, the above first implementation fj-c uses ry IJ as a compressor.
The same effect can be obtained by using a sliding piston type or a sliding vane type.

Furthermore, FIG. 3 shows a second embodiment of the present invention, and FIG.
'In the embodiment, two sub-compression chambers were provided in the compressor (1) to provide two-stage suction and compression of the intermediate pressure gas refrigerant, and one gas-liquid separator was used in the compressor (1).' It is configured to have one main compression chamber (26)' and one sub-compression chamber (2η') inside to perform heating operation by first-stage suction and compression of intermediate-pressure gas refrigerant, The same □ operation and effect as in the seventh embodiment can be achieved. - □As explained above, according to the present invention, an intermediate pressure gas injection system equipped with one or more gas-liquid separators is provided. [Type □] Tobong type - The space between the cylinder and rotor of a rolling stone type or sliding stone type compressor in a chamber device is divided into a main compression chamber and one or more sub compression chambers by means of a plurality of vanes. The gas refrigerant from the evaporator is compressed separately in the main compression chamber, and the intermediate pressure gas refrigerant from the gas-liquid separator is compressed separately in the sub compression chamber, resulting in cost reduction and compactness. Therefore, by lengthening the period during which the intermediate pressure gas refrigerant is sucked into the compressor, the entire optimal amount can be sucked, and heating capacity can be improved.Furthermore, after the intermediate pressure gas refrigerant is sucked, the intermediate pressure gas refrigerant can be directly sucked into the compressor. ] It is possible to increase the compression efficiency by compressing with a discharge pressure.Therefore, it is possible to make one improvement in heat pump type heating equipment.

[Brief explanation of drawings]

Fig. 1 is an overall configuration diagram showing a conventional intermediate pressure gas injection type heat pump type heating device, Figs. 2 and 3 show embodiments of the present invention, and Fig. 2 shows the entire structure of the first embodiment. The block diagram, FIG. 3, is an overall block diagram of the second embodiment. +1), +1)'...Compressor, (3)...Indoor heat exchanger, (4)...First expansion mechanism, (5)...Second expansion mechanism, (6)...Third expansion mechanism , (7)・High-pressure side gas-liquid separator, (8)・・low-pressure side gas-liquid separator, 1□ (9)・Outdoor heat exchanger, (4・・Cylinder N (23)
...Rotor, 1 (25) 1. <-y,
(26L ('26)・1.,ia,.1.i,(26
a) -1 car port, (26b)...Discharge boat, 127L +27)'...Sub compression chamber, (27a)
・Suction boat, (2'7b), Discharge port, (28
)--Sub compression chamber, (28a,)... Suction boat, (2
8b)...Discharge port, (29), (3()), +
31+...Collection piping.

Claims (1)

[Claims] (1) A rolling piston type or sliding vane type compressor (1), a condenser (3), two or more expansion mechanisms f4), f5)... and the expansion mechanism t4)
, one or more gas-liquid separators (7) disposed in each intermediate part of the evaporator (9), the gas refrigerant from the evaporator (9) and the gas-liquid Separator (7)...
The intermediate pressure gas refrigerant separated by
1)/ζζ Heat Posi 1 heating device, the cylinder (22) is and the rotor (23) respectively as suction ports (26a). (2'l'a)-- and discharge port (26b), (2'
7b), and one or more sub compression chambers (27), and the suction boat (26a) of the main compression chamber (26) is connected to the evaporator (9). On the other hand, the suction bow of the sub-compression chamber (27)...
2'7a)... are connected to the corresponding gas-liquid separators (7)..., and the main and sub compression chambers (26+, (2
Each discharge bow 1- (26b), (2'i'
b)...A heat pump type heating device characterized in that the entire set is connected to a condenser (3).