KR20040079327A - Gas engine driving type air conditioner - Google Patents

Abstract

PURPOSE: A gas engine driving type air conditioning apparatus is provided to reduce harmful vibration generated in a connecting pipe connecting compressors and a heat exchanger. CONSTITUTION: A gas engine is driven by combustion of fuel gas. Compressors(13,13B) are driven by the gas engine. A heat exchanger exchanges heat for air-conditioning a refrigerant compressed by the compressors. A container(80) is installed in a refrigerant pipe connecting the compressors with the heat exchanger, having a suction port(80m) sucking the refrigerant discharged from discharge ports(19) of the compressors, and a hollow chamber(80p) communicated with the suction port. When pipe length from the discharge ports of the compressors to the suction port of the container is represented by L, and the velocity of sound in the refrigerant is represented by C, and rotating frequency of the compressors for one second is represented by N, the L is smaller than C/(2*N).

Description

Gas Engine Driven Air Conditioning Units {GAS ENGINE DRIVING TYPE AIR CONDITIONER}

The present invention relates to an air conditioner for operating a compressor for compressing a refrigerant by a gas engine.

Background Art Conventionally, a gas engine driven air conditioner has been provided as an air conditioner. The gas engine driven air conditioner includes a gas engine driven by combustion of gas as fuel gas, a compressor driven by the gas engine, and a heat exchanger capable of heat exchange for air conditioning the refrigerant compressed by the compressor. According to this, since the pulsation of a refrigerant | coolant is produced | generated with the operation | movement of a compressor, there existed a lot of vibrations in the pipe | tube which connects a compressor and a heat exchanger, or a vibration generate | occur | produced in the room side.

As a technique for preventing vibration, a technique (Patent Document 1) having a structure in which a discharge pipe of a compressor is connected to a plurality of inlets of an oil separator in a conventional refrigeration apparatus is known.

Moreover, in the gas engine drive type air conditioner, a technique is known in which two compressors are driven at different rotational speeds by one gas engine to prevent resonance of each compressor (Patent Document 2). Since this publication differs in the capabilities of the two compressors, it is described that the resonance of the two compressors can be prevented.

Further, in the rotary compressor, the gas passage hole of the rotor is a winding type having an advancing inclination angle θ, and an integer of the frequency pulsation wavelength twice the rotation frequency whose length 1 · 1 / sinθ is the fundamental frequency of the discharge pulsation. By setting angle (theta) so that it may double, the noise mechanism of the rotary compressor which made the discharge pulsation in the upper and lower space of the stator in phase is known (patent document 3).

In addition, in a rotary compressor having a valve which is radiated in the radial direction of the cylinder, the upper and lower ends of the cylinder or the cylinder contact surface of the upper and lower bearings for sealing the upper and lower ends of the cylinder communicate with the compression chamber in the cylinder. A plurality of spaces having lengths corresponding to one wavelength and three quarter wavelength components of the resonant frequency are provided, and each space maintains angles θ1 and θ2 satisfying the following equation starting from vanes, and the compression chamber in the cylinder The technique of the effect arrange | positioned so that it may open to is known (patent document 4).

θ1 = 360 ° × {1-v / (2fRπ)}

θ2 = 360 ° × {1 × 3v / (8fRπ)}

f is a structural system resonance frequency, R is a cylinder bore radius.

[Patent Document 1]

Japanese Patent Laid-Open No. 10-9715

[Patent Document 2]

Japanese Patent Laid-Open No. 10-220886

[Patent Document 3]

Japanese Patent Laid-Open No. 8-270585

[Patent Document 4]

Japanese Patent Laid-Open No. 10-37884

It is an object of the present invention to provide a gas engine driven air conditioning apparatus which is advantageous in suppressing harmful vibrations from a viewpoint different from the above-described method.

1 is a circuit diagram of a gas engine driven air conditioning apparatus.

Fig. 2 is a perspective view showing the piping in the vicinity of the buffer according to the first embodiment.

3 is a configuration diagram showing a gas engine, a first compressor, and a second compressor;

Fig. 4 is a configuration diagram showing the structure of the first bellows type pipe section.

Fig. 5 is a perspective view showing the piping in the vicinity of the oil separator in accordance with the second embodiment.

6 is a graph showing a test example.

<Explanation of symbols for the main parts of the drawings>

1: main circuit

11: gas engine

12: accumulator

13B: first compressor

13: second compressor

14: outdoor heat exchanger (heat exchanger)

17: indoor heat exchanger (heat exchanger)

61: Oil Separator

61m: suction port

61p: hollow room

80: buffer (container)

80m: suction port

80p: hollow room

101: first pipe

102: second pipe

103: confluence

(1) The gas engine driven air conditioning apparatus according to the present invention of the first aspect is

A gas engine driven by combustion of fuel gas,

A compressor driven by a gas engine,

A heat exchanger with heat exchanger for air conditioning the refrigerant compressed by the compressor,

A gas engine driven air conditioning apparatus provided in a refrigerant pipe connecting a compressor and a heat exchanger, and having a container having a suction port through which a refrigerant discharged from a discharge port of the compressor is sucked and a hollow chamber communicating with the suction port,

When the pipe length from the discharge port of the compressor to the suction port of the container is L [meter], the sound velocity in the refrigerant is C [meter / sec], and the rotation speed of the compressor in N for 1 second is

The above-mentioned L is set so that the relationship of L <C / (2 * N) is satisfied.

When the natural frequency of the refrigerant pulsation is fn, the sound velocity in the refrigerant is C [meter / sec], and the pipe length from the discharge port of the compressor to the suction port of the container is L [meter]. The natural frequency fn causing the vibration is basically represented by the following equation (1).

fn = C / (2 × L) (1)

Therefore, according to the gas engine drive type air conditioning apparatus which concerns on this invention of 1st aspect, in order to suppress the natural vibration of refrigerant pulsation which generate | occur | produces by the drive of a compressor, as a frequency fa of refrigerant pulsation, fa = C / (2 * It is preferable to set L so as not to satisfy the relationship of L).

Here, since the frequency of the refrigerant pulsation for 1 second corresponds to the rotation speed N of the compressor for 1 second, when L is set to satisfy the relationship of L <C / (2 × N), the natural vibration of the refrigerant This is suppressed and is advantageous for suppressing harmful vibrations in the refrigerant pipe and suppressing vibrations on the indoor unit side.

It is also conceivable to set L so as to satisfy the relationship of L > C / (2N), but L becomes large and the pipe length becomes long. In this case, it is not preferable in the relationship between piping cost and piping space.

(2) The gas engine driven air conditioning apparatus according to the present invention of the second aspect is

A gas engine driven by combustion of fuel gas,

A first compressor driven by a gas engine,

A second compressor driven by a gas engine,

A heat exchanger capable of heat exchange for coordinating the refrigerant compressed by the first compressor with the refrigerant compressed by the second compressor,

A gas engine driven air conditioning apparatus provided in a refrigerant pipe connecting a first compressor and a second compressor to a heat exchanger, and having a container having a suction port through which a refrigerant is sucked and a hollow chamber communicating with the suction port.

The pipe length from the discharge port of the first compressor to the suction port of the container is L1 [meter], the pipe length from the discharge port of the second compressor to the suction port of the container is L2 [meter] and the sound velocity in the refrigerant. When C [meter / second] is set, the rotational speed of the first compressor in 1 second is N1, and the rotational speed of the second compressor in 1 second is N2.

The above-mentioned L1 and / or L2 is set so that at least one of the relationship of L1 <C / (2 * N1) and the relationship of L2 <C / (2 * N2) is satisfied.

When the natural frequency of the refrigerant pulsation is fn, the sound velocity in the refrigerant is C [meter / sec], and the pipe length from the discharge port of the compressor to the suction port of the container is L [meter]. The natural frequency fn causing the vibration is basically represented by the following equation (1).

fn = C / (2 × L) (1)

Therefore, according to the gas engine drive type air conditioning apparatus which concerns on this invention of 2nd aspect, in order to suppress the natural vibration of refrigerant pulsation which generate | occur | produces by the drive of a compressor, as a frequency fa of refrigerant pulsation, fa = C / (2 It is preferable to set L1 and L2 so as not to satisfy the relationship of x L1) and fa = C / (2 x L2).

Here, since the frequency of the refrigerant pulsation for 1 second corresponds to the rotation speed N of the compressor for 1 second, the relationship of L1 <C / (2 × N), or L2 <C / (2N) Setting L1 and / or L2 so as to satisfy Mg is advantageous in suppressing natural vibration of the refrigerant, and is advantageous in suppressing harmful vibration of the refrigerant pipe and vibration of the indoor unit.

It is also conceivable to set L1 and L2 so as to satisfy the relationship of L1> C / (2 x N1) and the relationship of L2> C / (2 x N2), but L1 and L2 become large and the piping length becomes long. . In this case, it is not preferable in the relationship between piping cost and piping space.

According to the gas engine-driven air conditioning apparatus according to the present invention of the first aspect, based on the above description that L <C / (2 × N) relation is good, the pulsation of the refrigerant is suppressed to prevent harmful vibration such as piping. In order to suppress, L is preferably shorter.

Here, the form in which the oil separator which isolate | separates the oil contained in the refrigerant | coolant discharged from the discharge port of a compressor is provided in the piping can be employ | adopted. In this case, the oil contained in the refrigerant discharged from the discharge port of the compressor can be separated by an oil separator.

In addition, the container may adopt a form that is a buffer for noise provided between the oil separator and the compressor. Thus, when the buffer is provided between the oil separator and the compressor, it is advantageous to shorten the L, to suppress the natural vibration of the refrigerant pulsation, and further to suppress the harmful vibration in the piping and the like.

According to the gas engine driven air conditioning apparatus according to the present invention of the second aspect, it is preferable that L2 and L1 are set to different lengths (L1? L2). In particular, it is preferable that L2 is set shorter than L1 (L2 <L1). In this case, L2 may represent, for example, a length of 98 to 40%, preferably a length of 90 to 60% with respect to L1.

When the first compressor and the second compressor are driven by a common gas engine, the rotational speed of the first compressor for one second and the rotational speed of the second compressor for one second are basically the same as long as the transmission efficiency is the same. It is often lost. In this case, there is a fear that the pulsation of the refrigerant generated in the first compressor and the pulsation of the refrigerant generated in the second compressor interfere with each other to form a large pulsation. Therefore, as described above, when L1 and L2 are different lengths, it is advantageous to solve the above problem of interference. For example, if L2 is set shorter than L1 (L2 < L1), it is advantageous to solve the above problem of interference.

According to the gas engine drive air conditioning apparatus which concerns on this invention of 2nd aspect, in a 2nd compressor, the pressure pulsation of a refrigerant | coolant may be comparatively larger than a 1st compressor depending on the specification of a compressor. Here, based on the above-mentioned description that L <C / (2 * N) relationship is good, L is preferably shorter in order to suppress harmful vibrations, such as piping while suppressing piping space.

Here, when L2 of the second compressor having a relatively large pressure pulsation of the refrigerant is set to be shorter than L1 of the first compressor having a relatively small pressure pulsation of the refrigerant (L2 <L1), the harmful vibration caused by the second compressor may be reduced. It is more advantageous for suppression.

According to the gas engine-driven air conditioning apparatus according to the present invention of the second aspect, the shorter the L is, in order to suppress harmful vibrations such as piping based on the above-described substrate. As described above, a form in which an oil separator for separating oil contained in the refrigerant discharged from the discharge port of the compressor is provided can be adopted. In this case, the oil contained in the refrigerant discharged from the discharge port of the compressor can be separated by an oil separator. In this case, the container may take the form of a buffer for noise provided between the oil separator and the first compressor and the second compressor. Thus, when the buffer is provided between the oil separator, the first compressor and the second compressor, the L1 and L2 are further shortened, which is advantageous in suppressing the natural vibration of the refrigerant pulsation, and the harmful vibration in the piping and the like. It is more advantageous to suppress.

<First Embodiment>

Hereinafter, an embodiment of the present invention will be described with reference to FIGS. The air conditioner according to the present embodiment is a gas engine driven air conditioner. First, with reference to FIG. 1, the main circuit 1 which concerns on a gas engine driven air conditioning apparatus is demonstrated. The main circuit 1 performs cooling or heating, and includes an outdoor unit 10 and an indoor unit 16. The outdoor unit 10 includes a gas engine 11 serving as a driving unit driven by combustion of fuel gas, an accumulator 12 accommodating refrigerant in a state in which a gaseous refrigerant and a liquid refrigerant are separated, and a gas engine 11. And a fixed displacement first compressor 13B for sucking and compressing the gaseous refrigerant of the accumulator 12 along with the driving, and a variable displacement agent for sucking and compressing the gaseous refrigerant of the accumulator 12. It has as a basic element the 2 compressor 13 and the outdoor heat exchanger 14 as a heat exchanger which heat-exchanges a refrigerant for air-conditioning. The compressors 13 and 13B are scroll rotary compressors and are interlocked by the gas engine 11 via timing belts. The blast furnace gas engine 11 functions as a common drive source for the compressors 13 and 13B.

The indoor unit 16 of the main circuit 1 has, as a basic element, an indoor heat exchanger 17 serving as a heat exchanger for performing heat exchange of a refrigerant for air conditioning, and an expansion valve 18 for expanding the refrigerant.

The suction port 15 of the first compressor 13B and the suction port 15 of the variable displacement compressor 13 are connected to the suction port 12a of the accumulator 12 by a passage 1v.

As shown in Fig. 1, the bypass passage 3 is for performing a bypass operation for returning the excess refrigerant of the variable displacement compressor 13 to the accumulator 12. The bypass passage 3 is provided in the main circuit 1 so as to connect the discharge port 19 of the variable displacement compressor 13 and the bypass port 12b of the accumulator 12. The bypass passage 3 is provided with a displacement control valve 4 so as to be located between the compressor 13 and the accumulator 12.

According to the air conditioning load (cooling load or heating load) of the main circuit 1, the rotation speed of the compressors 13 and 13B is controlled by a control system. In addition, according to the air conditioning load (cooling load or heating load) of the main circuit 1, opening / closing of the capacity control valve 4 of the bypass 3 is controlled by the control system. For this reason, the bypass port 12b of the accumulator 12 passes through the bypass passage 3 without supplying the excess refrigerant compressed by the variable displacement compressor 13 to the main circuit 1 during the bypass operation. ), Thereby restricting the flow rate of the refrigerant supplied to the main circuit 1.

Next, a basic path of the main circuit 1 when cooling the room will be described. When the gas engine 11 is driven by fuel gas, the first compressor 13B and the second compressor 13 are driven, and the gaseous refrigerant of the accumulator 12 is discharged from the intake port 12a of the accumulator 12. It is suctioned and compressed by the compressors 13 and 13B. The refrigerant compressed to high temperature and high pressure is discharged from the discharge ports 20 of the compressors 13 and 13B to reach the passage 1a and the oil separator 61. In the oil separator 61, oil is separated from the refrigerant. The refrigerant from which the oil is separated reaches the outdoor heat exchanger 14 through the first port 62a and the passage 1b of the four-way valve 62, and the high temperature and high pressure refrigerant is cooled by the outdoor heat exchanger 14 to exchange heat. And liquefy. The refrigerant having liquefied advances to the expansion valve 18 through the passage 1c, the filter drier 63, the ball valve 65A, the passage 1d, and the strainer 17n, and in the expansion valve 18, It expands and becomes a low temperature. The coolant that has become low temperature passes through the strainer 17m to the indoor heat exchanger 17, and heat exchanges with the indoor heat exchanger 17 to cool the room, and further, the passage 1e, the ball valve 65B, and the passage 1f. The return port 12c of the accumulator 12 through the third port 62c of the four-way valve 62, the second port 62b of the four-way valve 62, the double tube heat exchanger 67, and the passage 1h. Return to The returned refrigerant is stored in the accumulator 12 in a state separated into a liquid refrigerant and a gas refrigerant.

Next, a basic path of the main circuit 1 when heating the room will be described. When the gas engine 11 is driven by the fuel gas, the compressors 13 and 13B are driven, and the gaseous refrigerant of the accumulator 12 is sucked into the suction port 12a of the accumulator 12 and the compressors 13 and 13B. Is compressed. The refrigerant compressed to high temperature and high pressure is discharged from the discharge ports 20 of the compressors 13 and 13B to reach the passage 1a and the oil separator 61. As described above, the oil is separated from the refrigerant in the oil separator 61. The refrigerant from which the oil is separated reaches the indoor heat exchanger 17 through the passage 1f, the ball valve 65B, and the passage 1e through the third port 62c of the four-way valve 62, and the indoor heat exchanger. Heat exchanged to (17) to release heat to the room to heat the room. Then, the refrigerant passing through the indoor heat exchanger 17 reaches the expansion valve 18 through the strainer 17m, expands to the expansion valve 18, passes through the strainer 17n, passes the passage 1d, and the ball valve 65A. ), Through the filter drier 63 'and the passage 1c to the outdoor heat exchanger 14, and also to the first port 62a, the second port 62b of the four-way valve 62, the double tube heat exchanger 67 ) And the return port 12c of the accumulator 12 through the passage 1h. The returned refrigerant is stored in the accumulator 12 in a state separated into a liquid refrigerant and a gas refrigerant.

When the outdoor temperature is considerably low at the time of heating, the liquid flow rate adjusting valve 70 is opened. As a result, the refrigerant in the passage 1d passes through the liquid flow rate adjusting valve 70 to the passage 1k so as not to pass through the outdoor heat exchanger 14, and accumulates through the double tube heat exchanger 67 and the passage 1h. It returns to the return port 12c of (12).

Next, description is given about the capacity control valve 4 installed in the bypass passage 3. The displacement control valve 4 is provided in the bypass passage 3 connected to the discharge port 19 of the variable displacement second compressor 13. In accordance with the air-conditioning load of the main circuit 1, opening and closing of the displacement control valve 4 of the bypass 3 is controlled. In the case of returning to the accumulator 12 without supplying the excess refrigerant compressed by the variable displacement second compressor 13 to the main circuit 1, the capacity control valve 4 is opened. When the capacity control valve 4 is opened in this way, the excess refrigerant compressed by the variable displacement second compressor 13 is bypassed from the discharge port 19 of the variable displacement second compressor 13. (3) flows in the direction of arrow W1, flows from the refrigerant inflow port 40a of the capacity control valve 4 to the refrigerant outflow port 40b, and also passes through the bypass port 12b and returns to the accumulator 12. As a result, the refrigerant flow rate per unit time discharged from the variable displacement second compressor 13 to the main circuit 1 is varied.

2, the main part of the refrigerant pipe is explained. As shown in Fig. 2, the oil separator 61 is installed in a refrigerant pipe connecting the compressors 13, 13B and the heat exchangers 14, 17. As can be understood from Fig. 2, the oil separator 61 has a suction port 61m and a hollow chamber 61p having a large volume communicating with the suction port 61m.

The refrigerant used in the compressors 13 and 13B contains an oil that functions as a lubricating oil. This is to facilitate the mechanism operation in the compressors 13 and 13B. Therefore, the refrigerant discharged from the discharge port 19 of the compressors 13 and 13B contains oil.

Here, as can be understood from Fig. 2, the suction port 61m of the oil separator 61 has a refrigerant discharged from the discharge port 19 of the second compressor 13 of the variable displacement type in the direction of arrow K2, or a fixed capacity. The refrigerant discharged in the direction of the arrow K1 from the discharge port 19 of the first compressor 13B of the equation is sucked in. The oil separator 61 separates the oil and the refrigerant contained in the refrigerant.

Here, as shown in FIG. 2, the refrigerant pipe connecting the oil separator 61, the first compressor 13B, and the second compressor 13 has a discharge port 19 of the fixed capacity type first compressor 13B. And a first pipe 101 connecting the confluence unit 100 with the second pipe 102 connecting the discharge port 19 and the confluence unit 100 of the variable displacement second compressor 13, One conduit tube 103 connecting the confluence unit 100 and the suction port 61m of the oil separator 61 is provided. The confluence part 100 has a Y shape.

As shown in Fig. 2, one conduit tube 103 connected to the oil separator 61 is provided with a buffer 80 as a container. The buffer 80 can function as a muffler for noise, and communicates with the suction port 80m through which the refrigerant discharged from the discharge port 19 of the compressors 13 and 13B is sucked and the suction port 80m. It has a large hollow chamber 80p. The suction port 80m is disposed above the buffer 80.

As shown in Fig. 2, the buffer 80 is disposed in the vicinity of the oil separator 61 in a state along the oil separator 61. The discharge port 80u of the buffer 80 is disposed below the buffer 80 and communicates with the suction port 61m of the oil separator 61 by the joining pipe 103.

As shown in Fig. 2, the first pipe 101 has a first bellows pipe portion 201 and a second bellows pipe portion 202 arranged in series. The second pipe 102 has a first bellows pipe portion 201B and a second bellows pipe portion 202B arranged in series.

As shown in Fig. 4, the first bellows-type pipe 201 is arranged coaxially with the main body 300 having a plain yarn 300a connected to the smooth tube and the outer circumferential side of the plain yarn main body 300. Soldering for joining the cylindrical body 301 to be surrounded, the tubular connector 302 which forms the cylindrical shape surrounding the outer periphery of the shaft end part of the cylindrical body 301, and the plain pipe main body 300, the cylinder 301, and the connector 302 mutually. It has the junction part 303 formed in the part. Because of this structure, the shaft length of the plain pipe main body 300 is fixed, and thus the plain pipe main body 300 is prevented from being excessively extended by the pressure of the refrigerant.

The said plain pipe main body 300 has the advantage compared with a rigid pipe, it has flexibility, has absorbability in the radial direction, and reduces the stress load with respect to the connection part in piping. However, the plain pipe main body 300 of the first bellows-type pipe 201 has a characteristic that is easy to vibrate by harmful vibration or the like. If harmful vibration is generated, damage to the plain body main body 300 may occur, and the durability of the plain body main body 300 may not be sufficient. Also in this meaning, it is preferable to suppress noxious vibration in piping.

In addition, the first bellows-type pipe part 201 and the second bellows-type pipe part 202 also have the same structure and operation as in FIG. The first bellows pipe portion 201B and the second bellows pipe portion 202B also have the same structure and operation as in FIG.

As shown in Fig. 3, the fixed displacement first compressor 13B and the variable displacement compressor 13 have a transmission belt 11x by means of a pulley 11w mounted on the crankshaft of the gas engine 11. It is driven in conjunction with.

The fixed capacity type first compressor 13B is a compressor in which the flow rate of the refrigerant discharged per unit time is fixed if the rotational speed is the same. The variable displacement second compressor 13 is a compressor in which the flow rate of the refrigerant discharged per unit time varies even though the rotational speed is the same.

According to this embodiment, the piping length from the discharge port 19 of the fixed displacement first compressor 13B to the suction port 80m of the buffer 80 is L1 [meter]. The piping length from the discharge port 19 of the variable displacement second compressor 13 to the suction port 80m of the buffer 80 is L2 [meter]. The length between the buffers 80 is based on the hollow chamber 80p of the buffer 80 because it has a large flow path diameter and a large volume, and thus functions as an open end.

In addition, the sound velocity in the refrigerant at that temperature is set to C [meter / sec]. The sound velocity of the coolant also varies depending on the type of coolant, but when the coolant is the prone system R407C, the sound speed C in the gaseous coolant is generally 130 to 140 [meter / second] at 60 to 70 ° C. In addition, the rotation speed of the 1st compressor 13B in 1 second is made into N1. The rotation speed of the 2nd compressor 13 in 1 second is made into N2.

According to this embodiment, the frequency of the refrigerant pulsation for one second discharged from the first compressor 13B corresponds to the rotation speed N1 of the first compressor 13B for one second. In addition, the frequency of the refrigerant pulsation for one second discharged from the second compressor 13 corresponds to the rotation speed N2 of the second compressor 13 for one second.

For this reason, according to this embodiment, L1 and L2 are set so as to satisfy both of the relationship of L1 <C / (2 × N1) and the relationship of L2 <C / (2 × N1). As a result, as can be understood from the above description, the natural vibration of the refrigerant flowing through the pipe or the like is suppressed. Therefore, it is advantageous to suppress harmful vibrations in piping and the like due to natural vibrations of the refrigerant and to suppress vibrations on the indoor unit side.

It is also conceivable to set L1 and L2 so as to satisfy the relationship of L1> C / (2 x N1) and the relationship of L2> C / (2 x N2). Since it becomes long, it is not preferable in the relationship of piping cost and piping space.

In general, the second compressor 13 tends to have a relatively larger pressure pulsation of the refrigerant than the first compressor 13B. Based on the above-mentioned base material, in order to suppress harmful vibrations, such as piping, L is more preferable. According to this embodiment, L2 of the second compressor 13, which is a compressor on the side where the pressure pulsation of the refrigerant is relatively large, is transferred to the first compressor 13B, which is a compressor on the side of which the pressure pulsation of the refrigerant is relatively small. It is set to be shorter than L1 (L2 < L1). For this reason, it is further advantageous to suppress the harmful vibration resulting from the 2nd compressor 13 which is the compressor of the side in which the pressure pulsation of a refrigerant | coolant is relatively large. Moreover, as L2 / L1, it can set in the range of 0.95-0.4, or in the range of 0.8-0.6.

By the way, based on the above-described substrate, L is preferably shorter in order to suppress harmful vibrations such as piping. According to this embodiment, a buffer 80 that can function as a container is provided between the oil separator 61 and the first compressor 13B and the second compressor 13. Thus, when the buffer 80 is installed between the oil separator 61, the 1st compressor 13B, and the 2nd compressor 13, the oil separator 61 may be arrange | positioned in the position away from the compressors 13B, 13. Even at this time, it becomes more advantageous to shorten said L1 and L2, Furthermore, it is advantageous to suppress the natural vibration of a refrigerant | coolant, and it is further advantageous to suppress harmful vibration in piping etc.

According to the present embodiment, the tendency of the variable compressor type second compressor 13 to generate vibrations such as piping is easier than that of the fixed capacity type first compressor 13B. As described above, in order to reduce the harmful vibration, the shorter L length is effective. According to this embodiment, as shown in Fig. 2, L2 is set shorter than L1 (L2 < L1). This is advantageous in reducing harmful vibrations caused by the variable compressor type second compressor 13.

Further, according to the present embodiment, the first compressor 13B and the second compressor 13 are driven cooperatively with the common gas engine 11, and the pulley ratio is the same. The rotation speed of the first compressor 13B and the rotation speed of the second compressor 13 in one second are basically the same. In this case, the pulsation of the refrigerant generated in the second compressor 13 and the pulsation of the refrigerant generated in the first compressor 13B interfere with each other to form a large pulsation. Therefore, according to the present embodiment, as described above, when L2 is set shorter than L1 (L2 < L1), it is advantageous to solve the above-mentioned problem of pulsation interference.

Second Embodiment

5 shows a second embodiment. The second embodiment is basically the same as the first embodiment, and basically exhibits the same effects and effects. The common code | symbol is attached | subjected to a common site | part. 1, 3 and 4 can be applied mutatis mutandis to the second embodiment. As shown in Fig. 5, the noise buffer is not provided in this embodiment.

According to this embodiment, an oil separator 61 for separating oil from refrigerant discharged from the discharge port 19 of the first compressor 13B and the discharge port 19 of the second compressor 13 is provided as a container. have.

The piping length from the discharge port 19 of the 1st compressor 13B to the suction port 61m of the oil separator 61 is set to L1 [meter]. The piping length from the discharge port 19 of the 2nd compressor 13 to the suction port 61m of the oil separator 61 is set to L2 [meter]. The sound velocity in the refrigerant is set to C [meter / second]. The rotation speed of the 1st compressor 13B in 1 second is set to N1. The rotation speed of the 2nd compressor 13B in 1 second is set to N2.

According to this embodiment, it is set so as to satisfy both the relationship of L1 < C / (2xN1) and the relationship of L2 < C / (2xN2). In this way, the pulsation of the refrigerant discharged from the discharge port 19 of the first compressor 13B and the pulsation of the refrigerant discharged from the discharge port 19 of the second compressor 13 can be suppressed. Furthermore, it is advantageous in suppressing harmful vibration in piping etc.

Also in this embodiment, it is set in the relationship of L2 <L1. This is further advantageous in suppressing harmful vibrations caused by the second compressor 13 on the side where the pressure pulsation of the refrigerant is relatively large. Alternatively, L2 / L1 can be set within the range of 0.95 to 0.4 or within the range of 0.8 to 0.6.

<Test Example>

In the test example, the relationship between the rotation speed of the gas engine 11 and the magnitude | size of the pressure pulsation of a refrigerant | coolant is shown in FIG. 6 shows the magnitude (relative indication) of the pressure pulsation of the refrigerant at the outlet of the oil separator 61. 6 represents the rotational speed of the gas engine 11 for one minute. In relation to the power transmission ratio, the rotation speed of the first compressor 13B and the second compressor 13 becomes 1.9 times the rotation speed of the gas engine 11. The coolant is a prone system (R407C), and the sound velocity C in the coolant at about 70 ° C is about 130 [meter / second].

Here, the case where the rotation speed of the gas engine 11 is 1200 rpm is demonstrated. In this case, the rotation speed of the compressors 13 and 13B for 1 minute is 2280 rpm (1200 rpm x 1.9 = 2280 rpm). The rotation speed of the compressors 13 and 13B for one second is 38 rpm (2280/60 = 38 rpm). Here, C / (2 × N1) = 130 / (2 × 38) ≒ 1.7 meters. Therefore, in the case where the speed of the gas engine 11 is 1200 rpm, when L1 and L2 are less than 1.7 meters, it is advantageous to suppress the harmful vibration resulting from the natural vibration of refrigerant pulsation.

Next, the case where the rotation speed of the gas engine 11 is 1500 rpm is demonstrated. In this case, the rotation speed of the compressors 13 and 13B for 1 minute is 2850 rpm (1500 rpm x 1.9 = 2850 rpm). The rotation speed of the compressors 13 and 13B for 1 second is 48 rpm (2850/60 Hz 48 rps). Here, C / (2 × N1) = 130 / (2 × 48) ≒ 1.3 meters. Therefore, in the case where the rotation speed of the gas engine 11 is 1500 rpm, when L1 and L2 are less than 1.3 meters, it is advantageous to suppress the harmful vibration resulting from the natural vibration of refrigerant pulsation.

In other words, when the rotation speed of the gas engine 11 is 1200 to 1500 rpm, if L1 and L2 are out of the range of 1.3 to 1.7 meters, it is advantageous to suppress harmful vibrations caused by the natural vibration of the refrigerant pulsation.

In FIG. 6, characteristic line S1 shows the test result of the prior art which made L1 1.6 meters and L2 1.6 meters. The characteristic line S2 shows the test result of the test example corresponded to Example 1 which set L1 to 0.8 meters, L2 to 1.2 meters, and the buffer 80 was provided.

According to the prior art, as shown in the characteristic line S1 of Fig. 6, when the rotation speed of the gas engine 11 exceeds 1500 rpm for one minute, it is recognized that the pressure vibration of the refrigerant itself is reduced. The reason for this is not necessarily clear, but it is inferred that the pulsation suppression effect works under some influence when the rotation speed of the gas engine 11 is high, that is, when the rotation speed of the compressor is high. However, according to the prior art, the pulsation of the refrigerant has become considerably larger in 1200 to 1500 rpm, which is an area where the rotation speed of the gas engine 11 is high for one minute. When the pulsation of the refrigerant is large in this manner, the first bellows pipe portion 201, the second bellows pipe portion 202, the first bellows pipe portion 201B, and the second bellows pipe portion 202B are easily vibrated. There is a limit to the improvement of these durability. From this point of view, it can be considered that it is important to practically suppress the pulsation of the coolant in the region of 1200 to 1500 rpm in the rotational speed of the gas engine 11 for 1 minute.

On the other hand, according to the test results of the test example corresponding to the first embodiment, as shown in the characteristic line S2 of Fig. 6, the rotation speed of the gas engine 11 for 1 minute is 1200 to 1500 rpm, The pulsation of the refrigerant is considerably suppressed and the harmful vibration is reduced, and the above-described first bellows pipe portion 201, the second bellows pipe portion 202, the first bellows pipe portion 201B, and the second bellows pipe portion 202B are provided. It was confirmed that vibration of) was suppressed.

(Etc)

According to the above embodiment, as shown in FIG. 2, the fixed capacity first compressor 13B is connected to the first pipe 101, and the variable capacity second compressor 13 is connected to the second pipe ( 102, but is not limited thereto. On the contrary, a fixed capacity first compressor 13B is connected to the second pipe 102, and a variable capacity second compressor 13 is connected to the first pipe. It is good also as a structure connected to (101).

In addition, the piping form of an oil gas engine drive type air conditioning apparatus is not limited to what was shown in FIG. In addition, this invention is not limited only to the above-mentioned embodiment, It can change suitably and can implement in the range which does not deviate from the summary.

Sub-item 1 and a driving unit,

A compressor driven by the driving unit,

Heat exchanger and heat exchanger for air conditioning the refrigerant compressed by the compressor,

An air conditioner provided in a refrigerant pipe connecting said compressor and said heat exchanger, said container having a suction port through which a refrigerant discharged from a discharge port of said compressor is sucked and a hollow chamber communicating with said suction port,

The pipe length from the discharge port of the compressor to the suction port of the container is L [meter], the sound velocity in the refrigerant is C [meter / sec], and the rotation speed of the compressor in one second is set. When set to N,

The said L is set so that the relationship of L <C / (2 * N) is satisfy | filled. It is possible to provide an air conditioning apparatus that is advantageous for reducing harmful vibrations.

[Appendix 2] A driving unit,

A first compressor driven by the drive unit;

A second compressor driven by the driving unit;

A heat exchanger capable of exchanging heat for air conditioning the refrigerant compressed by the first compressor and the refrigerant compressed by the second compressor;

An air conditioner provided in a refrigerant pipe connecting the first compressor, the second compressor, and the heat exchanger, the container having a suction port through which a refrigerant is sucked and a hollow chamber communicating with the suction port,

The piping length from the discharge port of the first compressor to the suction port of the container is L1 [meter], the piping length from the discharge port of the second compressor to the suction port of the container is L2 [meter] and the refrigerant When the sound velocity at is set to C [meter / sec], the rotational speed of the first compressor for 1 second is N1, and the rotational speed of the second compressor for 1 second is N2.

The above-mentioned L1 and / or L2 is set so that at least one of the relationship of L1 <C / (2 × N1) and the relationship of L2 <C / (2 × N2) is satisfied. It is possible to provide an air conditioning apparatus that is advantageous for reducing harmful vibrations.

[Appendix 3] The gas engine drive according to claim 1, wherein L is set outside the range of 1.3 to 1.7 meters when the compressor is operated at a rotational speed of 2280 to 2850 rpm for 1 minute. Air conditioning system. It is possible to provide an air conditioning apparatus that is advantageous for reducing harmful vibrations. L may be 4 meters or less or 5 meters or less, for example.

[Appendix 4] The gas according to claim 4, wherein L1 and L2 are set outside the range of 1.3 to 1.7 meters when the compressor is operated at a rotational speed of 2280 to 2850 rpm for 1 minute. Engine driven air conditioning unit. It is possible to provide an air conditioning apparatus that is advantageous for reducing harmful vibrations. L1 and L2 can be 4 meters or less or 5 meters or less, for example.

As described above, according to the present invention, it is possible to provide a gas engine driven air conditioner that is advantageous for reducing harmful vibrations.

Claims (10)

A gas engine driven by combustion of fuel gas, A compressor driven by the gas engine, A heat exchanger capable of heat exchange for air conditioning the refrigerant compressed by the compressor; A gas engine driven air conditioning apparatus provided in a refrigerant pipe connecting the compressor and the heat exchanger, the container having a suction port through which the refrigerant discharged from the discharge port of the compressor is sucked and a hollow chamber communicating with the suction port; In The pipe length from the discharge port of the compressor to the suction port of the container is L [meter], the sound velocity in the refrigerant is C [meter / sec], and the rotation speed of the compressor in one second is set. When set to N, The above-mentioned L is set so that the relationship of L <C / (2 * N) is satisfied, The gas engine driven air-conditioning apparatus characterized by the above-mentioned. The gas engine driven air conditioner according to claim 1, wherein the vessel is an oil separator for separating oil contained in the refrigerant discharged from the discharge port of the compressor. The oil separator according to claim 1, further comprising an oil separator for separating oil contained in the refrigerant discharged from the discharge port of the compressor. The vessel is a noise buffer provided between the oil separator and the compressor, and the L is shortened by the installation of the buffer. A gas engine driven by combustion of fuel gas, A first compressor driven by the gas engine, A second compressor driven by the gas engine, A heat exchanger capable of exchanging heat for air conditioning the refrigerant compressed by the first compressor and the refrigerant compressed by the second compressor; In the gas engine driven air conditioning apparatus provided in the refrigerant pipe connecting the first compressor and the second compressor and the heat exchanger, the container having a suction port through which the refrigerant is sucked and a hollow chamber communicating with the suction port. , The piping length from the discharge port of the first compressor to the suction port of the container is L1 [meter], the piping length from the discharge port of the second compressor to the suction port of the container is L2 [meter] and the refrigerant When the sound velocity at is set to C [meter / sec], the rotational speed of the first compressor for 1 second is N1, and the rotational speed of the second compressor for 1 second is N2. The above-described L1 and / or L2 is set so as to satisfy at least one of the relationship of L1 <C / (2 × N1) and the relationship of L2 <C / (2 × N2). Air conditioning system. The gas engine driven air conditioner according to claim 4, wherein L2 and L1 are set to different lengths (L2? L1). The gas engine drive according to claim 4 or 5, wherein the second compressor has a pressure pulsation of the refrigerant relatively larger than that of the first compressor, and L2 is set shorter than L1 (L2 < L1). Air conditioning system. The gas engine driven air conditioner according to any one of claims 4 to 6, wherein the container is an oil separator for separating oil contained in the refrigerant discharged from the discharge port of the compressor. The oil separator according to any one of claims 4 to 6, wherein an oil separator for separating oil contained in the refrigerant discharged from the discharge port of the compressor is provided. The vessel is a noise buffer provided between the oil separator and the compressor, and the L is shortened by the installation of the buffer. A gas engine driven by combustion of fuel gas, A compressor driven by the gas engine, A heat exchanger capable of heat exchange for air conditioning the refrigerant compressed by the compressor; A gas engine driven air conditioning apparatus provided in a refrigerant pipe connecting the compressor and the heat exchanger, the container having a suction port through which the refrigerant discharged from the discharge port of the compressor is sucked and a hollow chamber communicating with the suction port; In The pipe length from the discharge port of the compressor to the suction port of the vessel is L [meter], the sound velocity in the refrigerant is C [meter / sec], and during operation of the gas engine driven air conditioner. When the practical speed range for 1 second of the compressor is from N _L to N _H (N _L <N _H ), L is, L <C / (2 × N _H ) or C / (2 × N _L ) <L Gas engine driven air conditioning apparatus is set to satisfy the relationship of. A gas engine driven by combustion of fuel gas, A first compressor driven by the gas engine, A second compressor driven by the gas engine, Gas engine type air provided in a refrigerant pipe compressed by the first compressor and a refrigerant pipe connecting the second compressor and the heat exchanger, the container having a suction port through which the refrigerant is sucked and a hollow chamber communicating with the suction port. In the regulating device, The pipe length from the discharge port of the first compressor to the suction port of the container is L1 [meter], the pipe length from the discharge port of the second compressor to the suction port of the container is L2 [meter], The sound velocity in the refrigerant is C [meter / sec], and the practical rotational speed range for 1 second of the first compressor during the operation of the gas engine driven air conditioner is N _L1 to N _H1 (N _L1 < N _H1 ), when the practical rotational speed range for one second of the first compressor during operation of the gas engine driven air conditioner is N _L2 to N _H2 (N _L2 <N _H2 ), L1 and / or L2, L1 <C / (2 × N _H1 ) or C / (2 × N _L1 ) <L1 With the relationship of, L2 <C / (2 × N _H2 ) or C / (2 × N _L2 ) <L2 Gas engine-driven air conditioning apparatus characterized in that it is set to satisfy at least one relationship among the relationship.