JPH0926232A - Air conditioning heat pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To eliminate a phenomenon of dry-out ascending vapor produces rumble at a section of a heat exchanger for recovering waste heat of an engine in an air conditioning heat pump, eliminate a state of phase separation in water/ water vapour, improve an action of a gas/liquid pump, reduce a pressure loss in a small-sized oil separator and further improve a rate of catching oil of a freezer. SOLUTION: A helical projection is arranged at an outer circumference of an inner pipe 1 acting as a refrigerant pipe constituting a heat exchanger for an engine waste heat. In addition, a helical projection is also arranged at an inner circumference of an outer pipe 2 acting as a cooling water pipe. At an oil separator R, a striking plate 7 is arranged at an upper part and a space (g) is provided between the striking plate 7 and the inner wall of an oil separator case 5.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioning heat pump, and more particularly to a heat exchanger for recovering engine waste heat during heating operation when a boiling water cooling type engine is used as a drive source of the air conditioning heat pump, and Regarding the structure of the oil separator.

[0002]

2. Description of the Related Art Conventionally, there is no heat pump using a boiling cooling engine as a drive source, and the structure of an engine waste heat recovery heat exchanger used in a conventional heat pump has a shallow groove as shown in FIG. The corrugated pipe was used as an inner pipe for the refrigerant, and the cooling water pipe arranged outside had a double pipe structure using a smooth pipe (see JP-A-6-201220).

Further, in the oil separator used in the above-mentioned conventional heat pump, the discharge gas is passed through a collecting material such as a mesh material or a porous body filled in the oil separator case to trap and trap the refrigerating machine oil. The subsequent refrigerating machine oil had a shape of being collected below the oil separator by gravity.
In addition, the gas was given a swirling flow for centrifugal separation.

[0004]

However, when the boiling heat engine is used as a drive source for the conventional heat pump together with the heat exchanger and the oil separator, there are the following problems. First, in the case of the structure of the conventional heat exchanger for recovering engine waste heat, the water flow rate is reduced to about 1/10 of that of the forced circulation type, and the cooling water heat transfer coefficient is significantly reduced. Also, the heat transfer tube is dried out by the steam. Further, the circulating water is cooled by the engine waste heat recovery heat exchanger, and the flow in the direction opposite to the circulation is induced, and the water flow becomes unstable. This tendency tends to become stronger as the performance of the heat exchanger for recovering engine waste heat improves. In addition, the cross-sectional area of the cooling water flow path in the heat exchanger for recovering engine waste heat is large, and because it is installed horizontally, the flow is slowed down and phase separation of water vapor and water occurs. The "pump" function is lost and instability increases. The circulating water is cooled by the heat exchanger for recovering engine waste heat, and the flow in the direction opposite to the circulation is induced, and the water flow becomes unstable. In addition, natural convection occurs in the cooling water cooled by the heat transfer tubes, and the temperature deviation of the cooling water occurs in the vertical plane, which reduces the effective temperature difference and further deteriorates the heat transfer performance. Of.

Further, in the case of an oil separator having a conventional structure, it does not matter if the volume of the oil separator is sufficiently large, but when miniaturization is promoted, the gas flow velocity in the oil separator is large and the pressure There was a problem of loss. Due to such a problem, a conventional air-conditioning heat pump using a boiling cooling engine as a drive source has not been realized.

[0006]

In order to solve the above problems, the present invention has the following structure. In claim 1, the inner tube for passing the refrigerant is a tube having a screw type outer shape, the outer tube fitted to the outside of the inner tube and passing the cooling water is a simple smooth tube, and the two tubes are doubled. A tubular heat exchanger is configured, which makes the circulating flow of cooling water spiral.
It promotes mixing of cooling water.

In the present invention, the inner pipe for passing the refrigerant is a pipe having a screw type outer shape, and the outer pipe fitted to the outside of the inner pipe and passing the cooling water is the screw projection of the inner pipe. A pipe having spiral inner surface protrusions in opposite directions is used, and a double pipe heat exchanger is constituted by both pipes, whereby a circulating water flow of the cooling water is spiraled to promote mixing of the cooling water.

According to the present invention, the refrigerant outlet pipe is projectingly opened from below the inside of the oil separator container, the collision plate is arranged above the refrigerant outlet pipe, and the oil return pipe is provided at the lower end of the oil separator container. In the oil separator having an opening, the collision plate is a rectangular plate or a concentric disc fixed to the inner surface of the oil separator container by abutting and fixing, and a gap is formed between the collision plate and the oil separator container.

According to a fourth aspect of the present invention, a refrigerant outlet pipe is projectingly opened from below inside the oil separator container, a collision plate is arranged above the refrigerant outlet pipe, and an oil return pipe is provided at a lower end of the oil separator container. In the oil separator with the opening, the collision plate is a rectangular plate or concentric disc that is fixed by abutting the inner surface of the oil separator container, and a gap is formed between the collision plate and the oil separator container. A cylindrical mesh tube is arranged along the inner circumference.

[0010]

Next, examples will be described. FIG. 1 is a circuit diagram of a refrigerant and cooling water of an air conditioning heat pump equipped with a heat exchanger for recovering engine waste heat according to the present invention, and FIG. , Which is a screw type outer shape) showing an embodiment of a heat exchanger for recovering engine waste heat, and FIG. 3 is an enlarged side view and a front view of the embodiment of FIG. 2 in which the outer periphery of the inner tube 1 is a screw type protrusion 1a. A cross-sectional view, FIG. 4 shows a spiral plate member 3 on the outer circumference of the inner pipe 1.
5 is an enlarged sectional view of a side surface and a front surface of the embodiment in which
6 is an enlarged cross-sectional view of a side surface and a front surface of an embodiment in which a spiral wire 4 is wound around the outer circumference of the inner tube 1, and FIG. FIG. 7 is a side sectional view showing a relational length between the screw type protrusion 1a of the inner tube 1 and the inner diameter of the outer tube 2, and FIG. 8 is a conventional sectional view of the embodiment. Drawing which shows the performance comparison of the heat exchanger for engine waste heat recovery and the heat pump for air conditioning of this invention, FIG. 9 is a side sectional drawing which shows the structure of the conventional heat exchanger for engine waste heat recovery.

FIG. 10 is a drawing showing a refrigerant circuit of an air conditioning heat pump, FIG. 11 is a front sectional view of an oil separator R relating to the air conditioning heat pump of the present invention, and FIG. 12 is a plan sectional view of the oil separator R of FIG. 13 is a front sectional view showing another embodiment in which the collision plate 7 of the oil separator R is disk-shaped, and FIG. 14 is the same oil separator R of FIG.
FIG. 15 is a front sectional view of an embodiment in which the collision plate 7 has a shape obtained by scraping the left and right sides of the disk, FIG. 16 is a plan sectional view of the oil separator R of FIG. 15, and FIG. 17 is the collision plate 7 side. 18 is a front sectional view of an embodiment in which the oil separator case 5 is swollen, FIG. 18 is a plan sectional view of the oil separator R of FIG. 17, and FIG. 19 is an embodiment in which the mesh tube 16 is attached to the inner wall portion of the oil separator case 5. 20 is a plan sectional view of the oil separator R of FIG. 19, and FIG. 21 is a comparative performance drawing of the oil separator R of the present invention and the prior art.

Referring to FIG. 1, an air conditioning heat pump driven by a boiling water cooling type gas engine will be described. The heat pump for air conditioning drives the engine with a gas fuel such as city gas, rotates the compressor C with the driving force of the gas engine, and heats the excess heat of the engine cooling water during engine heating to recover the waste heat of the engine. It is given to the refrigerant by S and used as a heat source for heating.

The flow of the refrigerant during cooling will be described. The compressor C is driven by the gas engine E to bring the refrigerant into a high-temperature high-pressure superheated steam state, and while passing through the oil separator R, the oil component mixed in the refrigerant for lubrication is separated. The high-temperature high-pressure superheated steam after separating the oil is guided to the engine waste heat recovery heat exchanger S by the four-way valve 20. While passing through the engine waste heat recovery heat exchanger S, the engine E
Heat from the cooling water. Then, it passes through the outdoor heat exchanger 24 and the outdoor heat exchange fan 29. While passing through the outdoor heat exchanger 24 and the outdoor heat exchange fan 29,
The high-temperature high-pressure superheated steam releases heat to be converted into a high-pressure liquid state, and the refrigerant releases heat into the atmosphere while the high-temperature high-pressure superheated steam changes to a high-pressure liquid state.

The high-pressure liquid refrigerant that has passed through the outdoor heat exchanger 24 passes through the heating expansion valve 27 and enters the liquid receiver 26. With the liquid receiver 26,
The refrigerant in the gas phase is separated, and only the refrigerant in the high pressure liquid state is supplied to the cooling expansion valve 28. In the cooling expansion valve 28, the refrigerant rapidly expands, and the refrigerant in a high-pressure liquid state becomes a low-temperature low-pressure vapor refrigerant, and while passing through the indoor unit 25, the refrigerant absorbs heat in the room to generate low-temperature low-pressure vapor. The refrigerant becomes vapor in a superheated state and returns from the four-way valve 20 to the accumulator A.
This cycle is repeated.

Next, the flow of the refrigerant during heating will be described. The four-way valve 20 is switched to the heating direction. The compressor C is driven by the gas engine E, and the refrigerant in the accumulator A becomes a high-temperature high-pressure superheated steam state. The refrigerant of the high-temperature high-pressure superheated steam is separated in oil by the oil separator R and reaches the indoor unit 25 from the four-way valve 20. The indoor unit 25
In the above, heat is released from the refrigerant of the high-temperature high-pressure superheated steam to the indoor air, and the refrigerant becomes a high-pressure liquid state. The emitted heat heats the room.

The refrigerant in the high-pressure liquid state is used for the cooling expansion valve 2
8 goes through and is in the liquid receiver 26. Next, in the heating expansion valve 27, the refrigerant in a high-pressure liquid state expands rapidly to become a low-temperature low-pressure vapor refrigerant, and the outdoor heat exchanger 2
4 and the portion of the outdoor heat exchange fan 29, heat is obtained from the outside air to become superheated steam.

At this time, if the temperature of the outside air is low and the vapor state of the low-temperature low-pressure vapor cannot obtain enough heat to become vapor in the overheated state, the heat exchanger for recovering engine waste heat While passing through S, it becomes superheated steam. In this case, the engine waste heat recovery heat exchanger S plays a role. The superheated refrigerant returns to the accumulator A, becomes a complete vapor phase, and returns to the compressor C. This cycle is repeated during heating.

The present invention relates to the structure of the heat exchanger S for recovering engine waste heat in the above structure.
In FIG. 9, a conventional engine waste heat recovery heat exchanger S is used.
Is shown. It has been conventionally composed of an inner tube 1 and an outer tube 2. The inner tube 1 which is a refrigerant tube is composed of a corrugated heat transfer tube, and a shallow groove 1b is formed on the outer circumference. However, since the conventional shallow groove 1b is itself a groove, the inner tube 1 and the outer tube 2 which is a cooling water tube are provided.
It was not possible to exert the effect of mixing the cooling water passing between and.

In the present invention, the inner pipe 1 which is the refrigerant pipe
A screw type protrusion 1a is forcibly projected on the outer periphery of the screw type protrusion 1a as shown in FIG. The heat exchanger S for recovering engine waste heat is mainly composed of an inner pipe 1, and an outer pipe 2 is loosely fitted around the inner pipe 1 with a certain gap therebetween to form the outer pipe 2 and the inner pipe 1. In order to secure a gap with the
Is fitted. Further, the left and right ends of the inner pipe 1 directly constitute the inlet and outlet of the refrigerant, but in the drawing,
The state of heating is shown, and the white arrow shows the passage direction of the refrigerant during heating.

The gap between the outer pipe 2 and the inner pipe 1 is a passage for the cooling water, and the cooling water moves from the cooling inlet 10 to the cooling water outlet 11. In the present invention, the gas engine E is of the cooling water boiling circulation type, and the cooling water that has become a high temperature inside the engine E is given an ascending force due to the high temperature so that it is provided outside the muffler 30. The exhaust heat exchanger 31, which is arranged, passes through the inside of the engine waste heat recovery heat exchanger S, and reaches the radiator 23.

In the radiator 23, the cooling water is cooled by the cooling air from the radiator fan, a descending force is applied to the cooling water, and the cooling water returns to the inside of the cooling passage of the engine E. 22 is a reverberating tank when blown out at high pressure,
21 is a cooling water tank. In such a configuration,
As in the conventional configuration of FIG. 9, there is only the shallow groove 1b. In such a conventional configuration, a cooling water circulating pump is provided and the cooling water boiling type reduces the water flow rate to one-tenth and the steam rises at a stroke, as compared with the case of the method of forced circulation. This causes a phenomenon called dryout.

The cause of such a problem is that the heat exchanger S for recovering engine waste heat cools the lubricating cooling water and induces a flow in the direction opposite to the circulation direction, which makes the flow of the cooling water unstable. Because of that. Such a tendency tends to be strengthened as the function of the engine waste heat recovery heat exchanger S is improved. Further, since the cross section of the cooling water passage in the heat exchanger S for recovering engine waste heat is large and is installed horizontally, the flow of the cooling water is decelerated, the water vapor and the water are phase separated, and the cooling water circulation is performed. It is also because the function of the "gas / liquid pump", which is the driving force of the, is lost, the cooling water does not move upward, and the instability increases. As a result, the flow of the cooling water is stopped, the cooling state is strengthened in this portion, and a flow in the direction in which the cooling water descends in the direction opposite to the circulation occurs.

Further, natural convection occurs in the cooling water cooled by the refrigerant, a large temperature deviation occurs in the vertical plane, and the lower portion of the outer tube 2 becomes a low temperature state. As a result, the effective temperature difference between the refrigerant and the cooling water decreases, and the heat transfer performance deteriorates.

According to the present invention, the outer circumference of the inner pipe 1 is the same as the conventional one.
Instead of the shallow groove 1b, a spiral protrusion such as the screw-shaped protrusion 1a protruding outward, the spiral plate member 3, or the spiral wire member 4 is formed. This allows
This causes a situation in which the flow of cooling water moves while rotating around the inner tube 1, and suppresses the phase separation of "water / steam". By suppressing the phase separation of “water / steam” in this way, it is possible to prevent the deterioration of the function of the “gas / liquid pump”. As a result, the decrease of heat transfer coefficient is prevented, the deterioration of cooling water flow stability due to the phase separation of "water / steam" is prevented, the occurrence of temperature deviation due to natural convection of the cooled circulating water is prevented, and the effective temperature It is possible to prevent the decline.

In the embodiment of FIG. 3, an enlarged view of the inner pipe 1 and the outer pipe 2 of FIG. 2 is shown. In this embodiment, three screw type protrusions 1a are provided on the outer circumference of the inner pipe 1, and the three screw type protrusions 1a are projected around the inner pipe 1 in a twisted state. As shown in FIG. 7, assuming that the outer diameter of the screw-type protrusion 1a has a diameter d, a small gap is generated between the outer diameter of the outer tube 2 and the diameter D of the outer tube 2.

The inner pipe 1 is a pipe through which the refrigerant passes, and the outer pipe 2 is a pipe through which cooling water passes. During heating, the refrigerant enters from the left side of the inner pipe 1 and escapes to the right side. Cooling water enters from the cooling inlet 10 on the right side and the cooling water outlet 1 on the left side.
It starts from 1. The inner tube 1 and the outer tube 2 are joined and supported by the left and right support rings 8 and 9.

In FIG. 4, the inner pipe 1 is constituted by a normal cylindrical pipe, and one spiral plate member 3 is fixed to the outer periphery of the inner pipe 1 by brazing or welding. Further, in the embodiment shown in FIG. 5, one spiral wire rod 4 is fixed by brazing or welding. In FIG. 6, it is not enough to configure the screw-type protrusion 1a on the outer circumference of the inner pipe 1, but the screw-type protrusion 2a is also provided on the inner circumference of the outer pipe 2, and by both,
It is configured to generate a twist in the flow of cooling water.

In FIG. 8, as in the present invention, the effect obtained by providing a spiral projection that twists the flow of cooling water on the outer circumference of the inner pipe 1 or the inner circumference of the outer pipe 2 is shown in the drawing. Shows. That is, it is shown that the heating capacity and the heat exchange amount for recovering engine waste heat are significantly improved in the present invention with respect to the boiler heat input, as compared with the prior art.

FIG. 10 shows a refrigerant circuit in the air conditioning heat pump, and particularly shows the position of the oil separator R. Then, in the present invention, the oil separator R is improved. That is, it is possible to sufficiently capture the refrigerator oil with a smaller size and a lower pressure loss than the conventional one. In the rotary type or scroll type compressor C, the refrigerating machine oil flowing in a state of being mixed with the refrigerant is important not only as a lubricating oil but also as a hydraulic oil and a sealant, and a flow rate of 10% (weight ratio) or more of the refrigerant is required. It circulates. However, after exiting the compressor C, a harmful effect such as deterioration of heat exchange performance appears. Therefore, an oil separator R is provided at the outlet of the compressor C to separate refrigerating machine oil and return it to the suction side of the compressor C. Has been taken.

However, there are problems such as insufficient oil capture rate and pressure loss problem. The present invention relates to a structure of an oil separator R that solves these problems, and promotes the adhesion of oil droplets to the wall surface to improve the trapping rate of refrigerating machine oil without increasing the pressure loss. Conventionally, when the refrigerant gas is passed through a collecting material such as a mesh material or a porous body to be downsized, the gas flow velocity in the oil separator R is increased and the pressure loss is increased. In the present invention, the collision plate 7 is arranged inside the oil separator case 5, and the gap g is provided between the oil separator case 5 and the collision plate 7 to generate a turbulent flow in the flow of the refrigerant gas to reduce the pressure. It aims to improve the capture rate of refrigerating machine oil without causing loss.

Further, by increasing the diameter of the inflow pipe, the flow velocity of the inflow gas can be reduced, so that the amount of oil mist generated can be reduced, the diameter of the oil droplets can be increased, and the refrigeration can be increased. The machine oil capture rate can be improved. In the embodiment of FIGS. 11 and 12, the inlet pipe 13 from the compressor C is provided in the upper part of the oil separator case 5, and the outlet pipe 6 to the condenser is provided below. The outlet pipe 6 projects inward to a level higher than the center of the oil separator case 5, and a collision plate 7 is fixed inside the oil separator case 5 with a gap from the upper end of the outlet pipe 6. There is.

As shown in FIG. 12, the collision plate 7 has a structure in which four corners of a rectangular plate are fixed to the inner diameter of the oil separator case 5, and between the collision plate 7 and the inner diameter of the oil separator case 5, Four arc-shaped voids g are formed. The refrigerant gas flowing from the inlet pipe 13 collides with the collision plate 7, the speed is suppressed, and the refrigerant gas flows into the lower chamber through the gap g. In the case of the present invention, the refrigerant moves to the lower chamber after passing through the gap g between the collision plate 7 and the inner wall of the oil separator case 5, so that the contact of the refrigerant contacting the inner wall of the oil separator case 5 The area is large, and the refrigerating machine oil is captured while passing through the gap g. Further, since the flow of the refrigerant gas is made uniform, the capture rate reaches 1.3 times that of the conventional one. Then, the refrigerating machine oil trapped in the lower chamber of the oil separator case 5 and descending is recirculated from the oil return ring 12 to a position in front of the compressor C.

The gap g between the oil separator case 5 and the collision plate 7 is a large factor, and if the flow velocity is too high,
The refrigerant gas is vigorously stirred in the lower chamber. If the amount is too small, the amount of refrigerating machine oil directly sucked through the opening of the outlet pipe 6 increases. It is preferable that the gap g has a cross-sectional area of about 0.5 to 0.8 cm 2 per 1 KW of cooling capacity. Further, when the volume of the lower chamber is too small, the flow of gas in the lower chamber becomes vigorous, and the trapping performance of the refrigerating machine oil deteriorates. The volume of the lower chamber needs to be 13 cubic centimeters or more per 1 kW of cooling capacity. Further, the diameter of the inlet pipe 13 is set to about 7 m / s, which is about half the inflowing gas velocity compared with the conventional one. With such a configuration, it is not necessary to fill the inside of the oil separator case 5 with a mesh material or a porous body as in the conventional case.

In the embodiment shown in FIGS. 13 and 14,
The collision plate 7 inside the oil separator case 5 is formed into a disc shape, and the left and right two points are fixed by the fixed coupling body 14,
An annular space g is formed. In the embodiment shown in FIGS. 15 and 16, the collision plate 7 is formed by cutting the left and right sides of a disc-shaped plate into an arc shape to form a cross section of a drum. Also, FIG.
7 and the embodiment shown in FIG. 18, the collision plate 7 is
5, the same as in the case of FIG. 16, but below the position where the collision plate 7 is arranged, the expansion protrusion 15 is formed in the oil separator case 5 on the side of the upper end position of the outlet pipe 6. . This also exerts the effect of improving the capture rate.

In the embodiment shown in FIGS. 19 and 20,
The collision plate 7 has the same shape as that of the embodiment of FIGS. 11 and 12, but the mesh tube 1 is formed on the inner surface of the oil separator case 5.
6 are arranged. The mesh cylinder 16 is not arranged on the entire inner surface of the oil separator case 5, but is arranged cylindrically on the inner wall portion of the oil separator case 5.

[0036]

As described above, the present invention has the following advantages. According to the first and second aspects of the invention, a situation occurs in which the flow of cooling water moves around the inner tube 1 while rotating, and phase separation of "water / steam" is suppressed. By suppressing the phase separation of “water / steam” in this way, it is possible to prevent the deterioration of the function of the “gas / liquid pump”. As a result, the decrease of heat transfer coefficient is prevented, the deterioration of cooling water flow stability due to the phase separation of "water / steam" is prevented, the occurrence of temperature deviation due to natural convection of the cooled circulating water is prevented, and the effective temperature It is possible to prevent the decline. Further, inside the heat exchanger S for recovering engine waste heat, it is possible to eliminate the phenomenon of dry-out in which air moves while making a noise.

Since the third and fourth aspects are configured, the collision plate 7 is arranged inside the oil separator case 5, and the gap g is provided between the oil separator case 5 and the collision plate 7.
By providing the above, the turbulent flow is generated in the flow of the refrigerant gas, and the trapping rate of the refrigerating machine oil can be improved without generating the pressure loss. Also, by increasing the diameter of the inflow pipe, the flow velocity of the inflow gas can be reduced, so that it is possible to reduce the amount of oil mist generated, increase the oil droplet diameter, and capture the refrigerator oil. The rate can be improved. Further, unlike the conventional case, the mesh cylinder 16 is provided along the gap g between the collision plate 7 and the inner wall of the oil separator case 5 without filling the inside of the oil separator case 5 with the mesh material. The pressure loss can be reduced and the refrigerating machine oil capture rate can be improved.

[Brief description of drawings]

FIG. 1 is a circuit diagram of a refrigerant and a cooling water of an air conditioning heat pump equipped with an engine waste heat recovery heat exchanger of the present invention.

FIG. 2 is a diagram showing an embodiment of a heat exchanger for recovering engine waste heat in which the outer circumference of the inner tube is a screw-shaped protrusion having screw-shaped irregularities.

3 is an enlarged sectional view of a side surface and a front surface of the embodiment of FIG. 2 in which the outer circumference of the inner tube 1 is a screw type protrusion 1a.

FIG. 4 is an enlarged sectional view of a side surface and a front surface of an embodiment in which a spiral plate member 3 is wound around an outer circumference of an inner pipe 1.

FIG. 5 is an enlarged sectional view of a side surface and a front surface of the embodiment in which the spiral wire rod 4 is wound around the outer circumference of the inner pipe 1.

FIG. 6 is a view showing a screw type protrusion 1a provided on the outer periphery of the inner tube
FIG. 3 is an enlarged cross-sectional view of a side surface and a front surface of an embodiment in which a screw type protrusion 2a is also formed on the inner surface of the outer tube 2.

FIG. 7 is a side cross-sectional view showing a relational length between the screw-shaped protrusion 1a of the inner pipe 1 and the inner diameter of the outer pipe 2.

FIG. 8 is a drawing showing a comparison of performance between a conventional engine waste heat recovery heat exchanger and the air conditioning heat pump of the present invention.

FIG. 9 is a side cross-sectional view showing the configuration of a conventional engine waste heat recovery heat exchanger.

FIG. 10 is a drawing showing a refrigerant circuit of an air conditioning heat pump.

FIG. 11 is a front sectional view of an oil separator R according to the heat pump for air conditioning of the present invention.

FIG. 12 is a plan sectional view of the oil separator R of FIG.

FIG. 13 is a front sectional view showing another embodiment in which the collision plate 7 of the oil separator R has a disc shape.

FIG. 14 is a plan sectional view of the oil separator R of FIG.

FIG. 15 is a front cross-sectional view of an embodiment in which the collision plate 7 has a shape in which the left and right sides of the disk are scraped off.

16 is a plan sectional view of the oil separator R of FIG.

FIG. 17: Oil separator case 5 on the side of the collision plate 7
FIG. 3 is a front cross-sectional view of an embodiment in which the bulges are formed.

18 is a plan sectional view of the oil separator R of FIG.

FIG. 19 is a front sectional view of an embodiment in which a mesh tube 16 is attached to the inner wall portion of the oil separator case 5.

20 is a plan sectional view of the oil separator R of FIG.

FIG. 21 is a comparative performance drawing of the oil separator R of the present invention and the prior art.

[Explanation of symbols]

 C Compressor C S Engine waste heat recovery heat exchanger R Oil separator 1 Inner pipe (refrigerant pipe) 2 Outer pipe (cooling water pipe) 3 Spiral plate material 4 Spiral wire rod 5 Oil separator case 6 Switch case 7 Collision plate

Claims (4)

[Claims] 1. An inner tube for passing a refrigerant is a tube having a screw type outer shape, an outer tube fitted to the outside of the inner tube, through which cooling water passes, is a simple smooth tube, and a double tube is formed by both tubes. A heat pump for air conditioning, characterized in that it constitutes a mold heat exchanger, and thereby makes the circulating water flow of the cooling water spiral to promote mixing of the cooling water. 2. An inner tube for passing a refrigerant is a tube having a screw type outer shape, and an outer tube fitted to the outside of the inner tube and through which cooling water passes has a direction opposite to a screw projection of the inner tube. A heat pump for air conditioning, characterized in that a pipe having a spiral inner surface protrusion is formed, and a double pipe type heat exchanger is constituted by both pipes, and thereby a circulating water flow of the cooling water is made spiral to promote mixing of the cooling water. . 3. An oil in which a refrigerant outlet pipe is projectingly opened from below inside the oil separator container, a collision plate is arranged above the refrigerant outlet pipe, and an oil return pipe is opened at a lower end of the oil separator container. In the separator, a heat pump for air conditioning, characterized in that the collision plate is a rectangular plate or a concentric disc fixed to the inner surface of the oil separator container by abutting and fixing it, and a gap is formed between the collision plate and the oil separator container. 4. An oil in which a refrigerant outlet pipe is projectingly opened from below inside the oil separator container, a collision plate is arranged above the refrigerant outlet pipe, and an oil return pipe is opened at a lower end of the oil separator container. In the separator, the collision plate is a rectangular plate or a concentric disc that is fixed to the inner surface of the oil separator container by abutting and fixing, and a gap is formed between the collision plate and the oil separator container, and below the collision plate along the inner circumference of the oil separator container. The heat pump for air conditioning is characterized in that a cylindrical mesh tube is arranged.