JP2003056474A - Pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a relatively small pump reduced in weight. SOLUTION: A friction pump comprising a housing 101 and a force-feed member 103 coaxially accommodated inside the housing guides a fluid into a clearance between the inner peripheral surface of the housing 101 and the outer peripheral surface of the force-feed member 103 from one end side in the axial direction of the force-feed member 103 and forcibly feeds the fluid to the other end side in the axial direction of the force-feed member 103 by the relative rotation of the housing 101 and force-feed member 103. In this case, a motor stator 109 constituting a driving part of the force-feed member 103 is disposed further outside of the housing 101, and a motor rotor is disposed integrally with the force-feed member 103.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pump for boosting and discharging a fluid (mainly a liquid) by its fluid frictional force,
In particular, the present invention relates to a heat storage type or gas heat pump type, a pump that is applied to an air conditioner for automobiles (for car air conditioners) and is suitable for conveying a liquid refrigerant.

[0002]

2. Description of the Related Art Conventionally, in order to convey a low-pressure liquid refrigerant flowing in a refrigerant system to various air conditioners such as a heat storage type, a gas heat pump type, an automobile (for a car air conditioner), a liquid refrigerant is used. A pump has been used, and as such a liquid refrigerant pump, a rotary type liquid refrigerant pump is generally applied.

A rotary type liquid refrigerant pump sucks the liquid refrigerant into a pump chamber by a rotor that rotates in synchronization with the motor, and then gradually increases the pressure of the liquid refrigerant in the pump chamber as the rotor is eccentrically rotated and discharges the liquid refrigerant to the outside of the pump. It is designed to

However, in the rotary type liquid refrigerant pump, if the rotational speed of the rotor is increased and the flow speed of the liquid refrigerant is increased in order to have a high head so as to meet the pump specification conditions, the pulsation (pressure change) of the liquid refrigerant is caused. Has a problem that the pumping performance becomes unstable, the mechanical life becomes short, etc. due to the structure, and the head per rotation of the rotor (pressure difference (differential pressure) between the suction side and the discharge side of the liquid refrigerant) I couldn't make it bigger. In addition, when the liquid refrigerant that is the pressure-feeding medium is chlorofluorocarbon, CO ₂ , H ₂ O, or the like, its viscosity is much lower than that of oil or the like, and its compressibility is poor.

Therefore, in order to solve the above problems, the liquid refrigerant suction side is generated by the fluid frictional force between the liquid refrigerant and the threaded portion (thread groove) provided on the outer circumference of the rotor or the inner circumference of the housing. A screw type liquid refrigerant pump has been developed which produces a large differential pressure between the discharge side and the discharge side, and delivers the liquid refrigerant from the low pressure side (suction side) to the high pressure side (discharge side). A conventional screw type liquid refrigerant pump 16 will be described with reference to FIG.

As shown in FIG. 6, the substantially cylindrical housing 1 has an inlet A and an outlet B. A rotor member 6 having a pumping member 3, shaft portions 4 a and 4 b, and a shaft 5 is housed in the housing 1. The rotor member 6 is rotatably supported by annular bearing members 2 a and 2 b provided on the inner circumference of the housing 1. A male screw is provided on the outer circumference of the pressure feeding member 3 so as to send the liquid refrigerant from the suction port A side, that is, one end in the axial direction of the pressure feeding member 3 to the other end side, that is, the discharge port B side (from the left side to the right side in FIG. 6). It is processed. Further, the shaft 5 is connected to the pumping member 3 and the shaft portions 4a and 4b on the same axis,
A motor rotor 10, which is a mover of an electromagnetic motor that drives a rotor member, is fixed. That is, the shaft 5 to which the motor rotor 10 is fixed is rotated by the rotational driving force of the stator 9 that is the stator of the electromagnetic motor, and the rotor member 6 is rotated around the axis of the motor rotor 10. The bearing members 2a and 2b are the rotor members 6
Of the rotor member 6 during high-speed rotation of the shaft member 4a, 4b
The inner diameter is machined large enough to stably support the. Further, a plurality of through holes 7a, 7b through which the liquid refrigerant flows are provided in the side end surfaces of the bearing members 2a, 2b at regular intervals in the circumferential direction. The shaft 5 has a bearing member 2b.
A discharge hole 8 is provided for discharging the liquid refrigerant flowing out from the through hole 7b to the outside of the pump.

An annular member 11 having a smooth inner peripheral surface is arranged on the inner circumference of the housing 1 so as to be opposed to the pressure-feeding member 3 (to surround the outer peripheral surface of the pressure-feeding member 3). The gap 1 is formed between the outer periphery of the ring and the inner periphery of the annular member 11.
4 are formed. Further, a thrust bearing 13 is provided adjacent to the bearing member 2a on the suction port A side (left side in FIG. 6), and the thrust bearing 13 has a through hole corresponding to each through hole 7a of the bearing member 2. 12 are formed.

With the above structure, the conventional screw type liquid refrigerant pump 16 operates as follows. When the shaft 5 is rotated by the action of the electromagnetic motor including the stator 9 and the motor rotor 10, the integrally connected rotor member 6 rotates in the same direction. At this time, the liquid refrigerant flowing from the suction port A passes through the through hole 12 and the through hole 7a, is sucked into the housing 1, and enters the gap portion 14. Then, due to the rotational movement of the pressure feeding member 3, a fluid frictional force is generated in the liquid refrigerant in the gap portion 14, and the liquid refrigerant is pulled by the outer peripheral surface of the pressure feeding member 3 to cause a movement, and the pressure is generated in the gap portion 1.
As it goes through 4, the pressure gradually increases and becomes a high pressure. Then, the high-pressure liquid refrigerant passes through the through hole 7b, reaches the discharge hole 8, and is discharged to the outside of the pump.

[0009]

By the way, such a screw type liquid refrigerant pump 16 becomes large in size by including a stator and a motor rotor which constitute an electromagnetic motor, and also becomes heavy and lacks versatility. The point is the problem.

In view of the above problems, it is an object of the present invention to provide a pump that is relatively small and has a reduced weight.

[0011]

According to a first aspect of the present invention, there is provided a pump according to claim 1, an outer cylinder body, and a cylindrical body housed inside the outer cylinder body and having the same axis as the outer cylinder body. A fluid is introduced from one end in the axial direction of the columnar body between the inner peripheral surface of the outer cylindrical body and the outer peripheral surface of the cylindrical body, and the axis line of the cylindrical body is generated by relative rotation between the outer cylindrical body and the cylindrical body. In a pump having a pump part for pumping the fluid to the other end in the direction and a drive part for rotating the columnar body, a stator of an electromagnetic motor constituting the drive part is arranged further outside the outer cylinder body. The mover is integrated with the cylindrical body.

According to a second aspect of the present invention, there is provided the friction pump according to the first aspect, wherein the cylindrical body is magnetized to serve as a movable element.

According to a third aspect of the present invention, in the friction pump according to the first aspect, the movable element is embedded inside the cylindrical body.

According to the first aspect of the present invention, the performance of the pump including the electromagnetic motor including the mover and the stator is lowered by integrating the mover with the cylindrical body. Therefore, it is possible to reduce the size and weight.

According to a fourth aspect of the present invention, in the friction pump according to the first, second or third aspect, a concavo-convex portion is provided on at least one of the outer peripheral surface of the cylindrical body and the inner peripheral surface of the outer cylindrical body. It is characterized by being formed.

According to the fourth aspect of the present invention, the frictional force generated in the fluid by the relative rotation between the outer cylindrical body and the cylindrical body is at least one of the inner peripheral surface of the outer cylindrical body and the outer peripheral surface of the cylindrical body. It is obtained by the “uneven portion” formed on one side. In other words, the friction coefficient of the surface (flow passage surface) on which the “uneven portion” is formed is excessive compared to the friction coefficient inherent to the material in the smooth state, so that it is more effective for the fluid that is the pumping medium. It is possible to exert a fluid frictional force.

According to a fifth aspect of the present invention, in the friction pump according to the fourth aspect, a male thread is formed on the outer peripheral surface of the cylindrical body, and an inner peripheral surface of the outer cylindrical body is opposite to the spiral direction of the male thread. It is characterized in that a female screw is machined in the direction.

According to the fifth aspect of the present invention, the frictional force generated in the fluid by the relative rotation between the outer cylindrical body and the cylindrical body is formed on the inner peripheral surface of the outer cylindrical body and the outer peripheral surface of the cylindrical body, respectively. Obtained by "threading". In other words, the flow passage surface of the pump portion on which the fluid frictional force can be applied can be formed by a very simple machining means, and the pump according to the present invention can be efficiently manufactured. In addition, it is possible to suppress the pulsation of the fluid flowing through the pump unit to a significantly small level.

Moreover, since the respective screw machining directions formed on the inner peripheral surface of the outer cylindrical body and the outer peripheral surface of the cylindrical body are opposite to each other, the coefficient of friction in the pump portion is significantly increased. Therefore, even when a low-viscosity fluid (liquid refrigerant) such as CFCs, CO ₂ or H ₂ O is used as the pressure-feeding medium, it is possible to feed the fluid at a high head.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. First, an embodiment of a screw type liquid refrigerant pump according to the present invention will be described with reference to FIG. In FIG. 1, reference numeral 100 is a screw type liquid refrigerant pump of this example. In this screw type liquid refrigerant pump 100, reference numeral 101 is a substantially cylindrical housing having an intake port A and a discharge port B, and 106 is a rotor member housed in the housing 101. The rotor member 106 is
The pressure feeding member (columnar body) 103 and the shaft 105 of the pressure feeding member 103 are provided.

On both sides of the shaft 105 sandwiching the pressure-feeding member 103, shaft portions 104a having a diameter larger than that of the shaft 105,
04b is provided, and an annular bearing member 102a, 102 that rotatably supports the rotor member 106 via shaft portions 104a, 104b is provided on the inner peripheral wall of the housing 101.
b is provided. The bearing members 102a and 102b have a plurality of through holes 107a and 107b penetrating in the thickness direction.
Are provided at regular intervals in the circumferential direction. In addition, the bearing members 102 a and 102 b are the rotor members 106.
The inner diameters of the rotor members 106 are set sufficiently large so as to stably support the rotor member 106 during high speed rotation. Furthermore, a thrust bearing 113 is provided adjacent to the bearing member 102a on the suction port A side. Thrust bearing 1
A through hole 112 corresponding to the through hole 107a of the bearing member 102a is formed in the hole 13.

Outside the housing 101, the pressure feeding member 10 is provided.
Motor stator (stator) 1 so as to surround 3
09 are provided. Further, the pressure-feeding member 103 is magnetized by itself and is given a function as a motor rotor. The bearing member 102 b is provided inside the shaft 105.
A discharge hole 108 for flowing the liquid refrigerant flowing out from the through hole 107b to the discharge port B is formed.

A thread groove (male screw) 120 is provided on the outer peripheral surface of the pressure-feeding member 103 so as to deliver the liquid refrigerant from the suction port A side to the discharge port B side. A cylindrical member 121 having a thread groove (female screw) 121 a is provided on the inner peripheral surface of the housing 101 so as to be opposed to the pumping member 103 (to surround the outer peripheral surface of the pumping member 103). The cylindrical member 121 is made of resin, and the thread groove 121a is integrally molded when the cylindrical member 121 is formed, and is formed separately from the housing 101 and combined with each other. Then, the cylindrical member 12 press-fitted into the shaft 105
A gap (pump portion) 114 is formed between 0 and the cylindrical member 121 fixed to the housing 101.

The screw type liquid refrigerant pump 100 configured as described above operates as follows. Motor stator 10
When 9 and the pumping member 103 having the function of the motor rotor are caused to cooperate with each other to rotate the shaft 105, the integrally connected rotor member 106 rotates in the same direction. At this time,
Due to the action of the rotor member 106, the liquid refrigerant is sucked from the suction port A and discharged to the discharge port B. That is, due to the rotational movement of the pressure-feeding member 103, a fluid frictional force is generated in the liquid refrigerant in the gap 114, and the liquid refrigerant is pulled by the outer peripheral surface of the pressure-feeding member 103 to cause a movement, and the pressure gradually advances in the gap 114. It increases and becomes high pressure. Then, the liquid refrigerant having a high pressure passes through the through hole 107b of the bearing member 102b,
And it is discharged to the discharge port B through the discharge hole 108.

As described above, in the screw type liquid refrigerant pump 100 of this example, the pumping member 103 itself is magnetized to function as a motor rotor, thereby including the electromagnetic motor as a drive unit for driving the rotor member 106. The pump 100 can be reduced in size and weight without deteriorating the performance as a pump.

In the screw type refrigerant liquid pump 100 described above, the pumping member 103 itself is magnetized to function as a motor rotor. Instead, as shown in FIG. 2, the pumping member 103 is magnetically permeable. It is also possible to give the function as the motor rotor to the pressure-feeding member 103 by fitting and burying the mover (that is, the permanent magnet) 110a in the space 103a provided inside the pressure-feeding member 103 by using an excellent material. . In addition, the pumping member 103
When the device itself functions as a motor rotor, the pressure feeding member 1
03 may be manufactured and then magnetized, or the magnetized material may be cut out to form the pumping member 103.

The screw type refrigerant liquid pump 100 described above is used.
In the outer peripheral surface of the pressure-feeding member 103,
Is a cylindrical member 12 disposed inside the housing 101.
Although the thread groove 121a is formed on the inner peripheral surface of No. 1, in the present invention, the function as a pump can be obtained even if either of the thread grooves 120 and 121 is omitted. However, the thread groove 12
It is preferable that both 0 and 121 are provided because the coefficient of friction of the flow path is significantly increased, and thus the lift of the liquid refrigerant can be significantly improved.

Next, various air conditioners equipped with the screw type liquid refrigerant pump 100 according to one embodiment of the present invention will be described.

FIG. 3 is an example of a system diagram of a heat storage type air conditioner 232 to which the screw type liquid refrigerant pump 100 is applied. It is called a static heat storage device, and includes a heat storage device 212, an outdoor unit 213, and an indoor unit 214.
The heat storage device 212 has a heat storage tank 215 in which water 221 is stored and a heat transfer tube 222 is immersed in the water 221.
The liquid refrigerant pump 100 arranged between the heat transfer pipe 222 and the indoor unit 214, the gas pipe 234 and the liquid pipe 233 connecting the outdoor unit 213 and the indoor unit 214, and branched from the liquid pipe 233 and connected to the heat transfer pipe 222. The bypass liquid pipe 235 and the like are provided. The on-off valves 216, 217, 218 are respectively provided on the gas pipe 234 and the heat transfer pipe 222, the outdoor unit 213 and the heat transfer pipe 222, the heat transfer pipe 222 and the refrigerant liquid pump 100, and the bypass liquid pipe 235. , 219
Is provided. Further, the on-off valve 217 and the heat transfer tube 222
A diaphragm 220 is provided between them.

The indoor unit 214 has an indoor heat exchanger 226 connected to the heat transfer pipe 222 via a connecting gas pipe 231 and an opening / closing valve 216, and a heat storage device 212 and an indoor heat exchanger 226 via a connecting liquid pipe 230. A diaphragm 2 provided between
And 27. The outdoor unit 213 has a connection liquid pipe 228.
Outdoor heat exchanger 22 connected to the heat storage device 212 via
5, the compressor 223, and the connection gas pipe 229 are connected to the heat storage device 212, and the outdoor heat exchanger 225.
And a four-way switching valve 224 that connects the compressor 223.

With the above structure, the heat storage type air conditioner 2
32 operates as follows. During the indoor cooling operation, the gas refrigerant compressed and discharged by the compressor 223 passes through the four-way switching valve 224 as shown by a solid arrow and the outdoor heat exchanger 22.
5, and heat is dissipated there to be condensed and liquefied (liquefied refrigerant). The liquid refrigerant enters the heat storage device 212 through the connection liquid pipe 228, and passes through the liquid pipe 233, the opening / closing valve 219 provided in the liquid pipe 233, and the connection liquid pipe 230, and then the indoor unit 2
Enter 14. Then, after being adiabatically expanded by being throttled by the throttle 227, it enters the indoor heat exchanger 226, where the indoor air is cooled and evaporated and vaporized again. This gas refrigerant enters the heat storage device 212 via the connection gas pipe 231, passes through the gas pipe 234, returns to the outdoor unit 213 via the connection gas pipe 229, and passes through the four-way switching valve 224 to the compressor 2
Inhaled at 23.

On the other hand, during the indoor heating operation, the four-way switching valve 22
4, the gas refrigerant discharged from the compressor 223 is switched in the opposite direction to the above, and the four-way switching valve 2
24, connecting gas pipe 229, gas pipe 234, connecting gas pipe 2
31, indoor heat exchanger 226, throttle 227, connecting liquid pipe 23
0, the liquid pipe 233, the opening / closing valve 219, the connecting liquid pipe 228, the outdoor heat exchanger 225, and the four-way switching valve 224 in this order, and then the compressor 2
It is inhaled again at 23. The open / close valves 216, 21 of the heat storage device 212 are used during the cooling operation and the heating operation.
7, 218 are both closed, and the screw type liquid refrigerant pump 1
00 is stopped.

On-off valves 216, 2 during the ice making operation of the heat storage tank
17, the open / close valves 218 and 219 are closed, and the screw type liquid refrigerant pump 100 is stopped. The gas refrigerant discharged from the compressor 223 enters the heat storage device 212 via the four-way switching valve 224, the outdoor heat exchanger 225, and the connecting liquid pipe 228 as shown by the white arrow. Next, it enters the throttle 220 via the on-off valve 217 interposed in the bypass liquid pipe 235, adiabatically expands by being throttled by the throttle 220, and then enters the heat transfer pipe 222. Then, in the process of passing through the heat transfer tube 222, the water 221 is cooled to freeze the water around the heat transfer tube 222.
By forming 36, vaporization is performed. The vaporized gas refrigerant is sucked into the compressor 223 via the on-off valve 216, the gas pipe 234, the connecting gas pipe 229, and the four-way switching valve 224.

On the other hand, the compressor 22 is operated during the defrosting operation of the heat storage tank.
3 is stopped, and the screw type liquid refrigerant pump 100 is driven as described above. Then, the open / close valves 216 and 218 are opened and the open / close valves 217 and 219 are closed. Thus, the liquid refrigerant discharged from the screw type liquid refrigerant pump 100 enters the indoor unit 214 via the connection liquid pipe 230 as shown by the black arrow.
After being adiabatically expanded by the throttle 227, the indoor heat exchanger 226 cools the indoor air to evaporate it. And
After being condensed and liquefied by melting the freezing 236 in the process of entering the heat transfer tube 222 through the connection gas tube 231, the gas tube 234, and the opening / closing valve 216 and passing through the heat transfer tube 222,
It is sucked into the screw type liquid refrigerant pump 100 via the on-off valve 218. Since the screw type liquid refrigerant pump 100 according to the present invention is incorporated in the heat storage type air conditioner 232, even if a low viscosity fluid (liquid refrigerant) such as CFC, CO ₂ , H ₂ O is used as the refrigerant. It is possible to efficiently pump with a high head.

Next, the screw type liquid refrigerant pump 1 will be described with reference to FIG.
Gas heat pump type air conditioner 23 to which 00 is applied
An example of No. 7 will be described. In FIG. 4, one outdoor unit 238 and a plurality of (three in FIG. 4) indoor units 239 are connected via a header 240 by a refrigerant pipe line. The outdoor unit 238 includes a lower machine room 238a and an upper heat exchanger room 238b.

A compressor 242 driven by an engine (internal combustion engine) 241 includes an indoor heat exchanger 243 and a pressure reducing element 24.
4. Refrigerant pipeline of outdoor heat exchanger 245 and four-way switching valve 24
It is connected via 6. High pressure liquid pipe 247 of the refrigerant line
The refrigerant liquid pump 100, the bypass opening / closing valve 249, and the water heat exchanger 250 of the engine 241 are interposed in the branch pipe line 248 that is further branched, and the water heat exchanger 250 and the radiator 251 are connected to the engine via the three-way switching valve 252. It is connected in parallel to the cooling water pipe line 241. Three-way switching valve 252
Are proportionally controlled based on the pressure at the refrigerant outlet of the water heat exchanger 250. A first refrigerant on-off valve 253 opened during the heating operation and a second refrigerant on-off valve 254 opened during the cooling (cooling) operation are provided in parallel on the refrigerant outlet side of the water heat exchanger 250. The first refrigerant opening / closing valve 253 is provided between the four-way switching valve 246 and the indoor heat exchanger 243, while
The refrigerant on-off valve 254 is connected between the four-way switching valve 246 and the outdoor heat exchanger 245.

With the above structure, the gas heat pump type air conditioner 237 acts as follows. During the heating operation for heating or hot water supply, the bypass opening / closing valve 249 is opened, and a part of the high-pressure liquid refrigerant condensed in the indoor heat exchanger 243 is pumped to the water heat exchanger 250 of the engine 241 by the refrigerant liquid pump 100. . Then, the liquid refrigerant is heated by the water heat exchanger 250 to be gasified, and this refrigerant having a high temperature and high pressure is merged with the refrigerant discharged from the compressor 242, and is sent to the indoor heat exchanger 243 again, thereby heating capacity. Is improving. Further, the flow rate of the cooling water flowing through the water heat exchanger 250 and the radiator 251 in the cooling water pipe is controlled by the three-way switching valve 25
By adjusting with 2, the exhaust heat recovery of the water heat exchanger 250 is kept good, and the heating capacity is further improved.

On the other hand, during cooling (cooling) operation, a part of the high pressure liquid refrigerant condensed in the outdoor heat exchanger 245 is pumped to the water heat exchanger 250 of the engine 241 by the screw type liquid refrigerant pump 100. Since the high temperature engine cooling water is cooled by the liquid refrigerant, the engine cooling water radiator 251 is downsized. The liquid refrigerant that has been heat-exchanged with the engine cooling water and gasified merges with the refrigerant discharged from the compressor 242, is sent to the water heat exchanger 250 again, and is then condensed. That is, since it is the gas heat pump type air conditioner in which the water heat exchanger 250 for exchanging heat between a part of the high pressure liquid refrigerant and the high temperature cooling water of the engine 241, is incorporated, the exhaust heat of the engine 241 is recovered as a heat source for heating. This is a device that does not require a dedicated pipe for heating and can strongly heat the room with the indoor heat exchanger 243. Further, since the screw type liquid refrigerant pump 100 according to the present invention is incorporated in the gas heat pump type air conditioner 237, a low-viscosity fluid (liquid refrigerant) such as CFC, CO ₂ or H ₂ O is used as a refrigerant. Even if there is, it is possible to efficiently pump under a high head.

FIG. 5 is an example of a schematic system diagram of an automobile (car air conditioner) air conditioner 255 to which the screw type liquid refrigerant pump 100 is applied and which uses a natural refrigerant such as CO ₂ . As shown in FIG. 5, two refrigerant circulation paths consisting of a primary and a secondary (hereinafter referred to as “primary cycle 2
56 "and" secondary cycle 257 ". ).

In the primary cycle 256, a compressor 258, a condenser 259, an expansion valve 260 and an evaporator 261 are connected in series by a first refrigerant line 262. Also,
In the secondary cycle 257, the evaporator 261, the screw type liquid refrigerant pump 100, and the vehicle interior heat exchanger 263 are connected in series by the second refrigerant pipe line 264. Only the vehicle interior heat exchanger 263 is provided in the vehicle interior, and the other components are provided in the engine room.

With the above-mentioned structure, an air conditioner 25 for automobiles (for car air conditioners) using a natural refrigerant such as CO ₂
5 works as follows. During the cooling operation, the first refrigerant pipeline 26 compressed to a high temperature and high pressure by the compressor 258.
The gas refrigerant (eg, propane) flowing through 2 exchanges heat with the outdoor air in the condenser 259, is cooled, and is condensed and liquefied. The liquefied liquid refrigerant (hereinafter referred to as “liquid refrigerant a”) is brought to a low temperature / low pressure state by the expansion valve 260 and is sent to the evaporator 261. Then, in the evaporator 261, heat is exchanged with the liquid refrigerant (for example, a natural refrigerant such as CO ₂ ; hereinafter referred to as “liquid refrigerant b”) flowing through the second refrigerant pipe 264 of the secondary cycle 257, and the liquid refrigerant b. To cool. The liquid refrigerant a flowing through the first refrigerant pipe 262 is evaporated and vaporized by heat exchange in the evaporator 261, becomes a low-temperature low-pressure gas refrigerant a, and is sucked into the compressor 258 again. On the other hand, the liquid refrigerant b cooled in the evaporator 261 is sent under high pressure by the screw type refrigerant liquid pump 100 and flows into the vehicle interior heat exchanger 263. Then, heat is taken from the vehicle interior air passing outside the vehicle interior heat exchanger 263 to cool it. The liquid refrigerant b, which has taken heat, flows through the second refrigerant pipe 264 and returns to the evaporator 261 again, where heat is exchanged with the low-temperature low-pressure liquid refrigerant a. As described above, since the screw type liquid refrigerant pump 100 according to the present invention is incorporated in the automobile (car air conditioner) air conditioner 255, a low viscosity fluid (liquid refrigerant) such as CO ₂ and H ₂ O. Even if is used as a refrigerant, it is possible to efficiently pump under a high head.

As described above, as an example of an air conditioner to which the screw type refrigerant liquid pump 100 according to the embodiment of the present invention is applied, a heat storage type air conditioner 232, a gas heat pump type air conditioner 237 and an automobile (for a car air conditioner) Although the air conditioner 255 is used for the description, the present invention is not limited to these, and can be applied to various air conditioners that pump liquid refrigerant. Further, the pumping medium is not limited to the "liquid refrigerant" used in the description of the embodiments of the present invention, and the friction pump according to the present invention can be applied to fluid systems that pump various "fluids". Needless to say.

[0043]

As described above, the present invention has the following effects. By integrating the mover with the cylindrical body, the pump including the electromagnetic motor including the mover and the stator can be downsized and reduced in weight without deteriorating the performance of the pump.

The frictional force generated in the fluid by the relative rotation between the outer cylindrical body and the cylindrical body is caused by the "uneven portion" formed on at least one of the inner peripheral surface of the outer cylindrical body and the outer peripheral surface of the cylindrical body. can get. In other words, the friction coefficient of the surface (flow passage surface) on which the "uneven portion" is formed is excessive compared to the friction coefficient unique to the material in the smooth state, so it is very effective for the fluid that is the pumping medium. It is possible to exert a fluid frictional force on the.

The frictional force generated in the fluid by the relative rotation between the outer cylindrical body and the cylindrical body is obtained by the "screw processing" formed on the inner peripheral surface of the outer cylindrical body and the outer peripheral surface of the cylindrical body, respectively. That is, it is possible to form the flow path surface of the pump portion capable of exerting the fluid frictional force by a very simple machining means, and the pump according to the present invention can be efficiently manufactured. Moreover, the pulsation of the fluid flowing through the pump portion can be suppressed to a significantly small level.

Moreover, since the respective screw working directions formed on the inner peripheral surface of the outer cylindrical body and the outer peripheral surface of the cylindrical body are opposite to each other, the coefficient of friction in the pump portion is remarkably increased. Therefore, even when a low-viscosity fluid (liquid refrigerant) such as CFC, CO ₂ , or H ₂ O is used as the pressure-feeding medium, it can be pressure-fed at a high head.

[Brief description of drawings]

FIG. 1 is a cross-sectional structural diagram of a screw type liquid refrigerant pump according to an embodiment of the present invention.

FIG. 2 is a perspective view of a pumping member used in the screw type liquid refrigerant pump.

FIG. 3 is a system diagram of a heat storage type air conditioner to which a pump according to an embodiment of the present invention is applied.

FIG. 4 is a system diagram of a gas heat pump type air conditioner to which a pump according to an embodiment of the present invention is applied.

FIG. 5 is a schematic system diagram of an automobile (car air conditioner) air conditioner to which a friction pump according to an embodiment of the present invention is applied.

FIG. 6 is a sectional structural view of a conventional screw type liquid refrigerant pump.

[Explanation of symbols]

100 screw type refrigerant liquid pump 101 housing (outer cylinder) 103 pumping member (cylindrical body) 109 Motor stator (stator) 110a Motor rotor (mover) 114 Gap (Pump part) 120 thread groove (male thread) 121a Thread groove (female thread)

   ─────────────────────────────────────────────────── ─── Continued front page    F-term (reference) 3H040 AA09 BB00 CC09 CC21 DD01                 3H041 AA00 BB05 BB06 CC11 CC15                       CC20 DD01 DD05 DD10 DD11                       DD31 DD33

Claims (5)

[Claims] 1. An outer cylindrical body, a cylindrical body housed inside the outer cylindrical body and having the same axis as the outer cylindrical body, and an inner circumference of the outer cylindrical body from one end side in the axial direction of the cylindrical body. A pump portion that guides fluid between a surface and the outer peripheral surface of the cylindrical body, and pumps the fluid to the other end side in the axial direction of the cylindrical body by relative rotation of the outer cylindrical body and the cylindrical body; In a pump having a drive unit for rotating a body, a stator of an electromagnetic motor that constitutes the drive unit is disposed further outside the outer cylindrical body, and a mover is integrally disposed in the columnar body. A pump characterized by. 2. The pump according to claim 1, wherein the columnar body is magnetized to serve as a movable element itself. 3. The pump according to claim 1, wherein a mover is embedded inside the cylindrical body. 4. The pump according to claim 1, wherein an uneven portion is formed on at least one of an outer peripheral surface of the cylindrical body and an inner peripheral surface of the outer cylindrical body. . 5. A male screw is formed on the outer peripheral surface of the cylindrical body, and a female screw is formed on the inner peripheral surface of the outer cylindrical body in a direction opposite to the spiral direction of the male screw. 4. The pump according to 4.