JP2009063234A - Compressor lubricating system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor lubricating system capable of securing stable supply of a lubricant to a compressor and dissolving lubrication shortage in a crank chamber. <P>SOLUTION: This compressor lubricating system 101 comprises the compressor 1 comprising the crank chamber 15 inside, an oil separator 41 and an ejector 61. A supply port 61a of the ejector 61 is communicated with a discharge port 26 of the compressor 1, the discharge port 61b is communicated with the crank chamber 15 of the compressor 1, and a suction port 61c is communicated with the oil separator 41. The ejector 61 sucks the lubricant separated from a refrigerant by the oil separator 41, from the suction port 61c by action of negative pressure generated inside of the ejector 61 in circulating the refrigerant discharged from the compressor 1 from the supply port 61a to the discharge port 61b, mixes the refrigerant and the lubricant, and supplies them to the crank chamber 15 through the discharge port 61b. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a system for lubricating a compressor.

  A cooling system for an air conditioner used in an automobile or the like cools outside air by an endothermic action of a refrigerant in the cooling system. The refrigerant circulates through the cooling system by the action of a compressor included in the cooling system. The compressor sucks the refrigerant that has circulated through the cooling system, compresses and pressurizes the refrigerant, and discharges the refrigerant again to the cooling system.

The compressor includes in its housing a compression mechanism that compresses the sucked refrigerant and a drive mechanism that drives the compression mechanism. A crank chamber is formed in the housing, and a drive mechanism is included in the crank chamber.
The sliding part in the compressor needs to be lubricated with lubricating oil, but the lubricating oil that is soluble in the refrigerant is mixed with the refrigerant and distributed along with the refrigerant to lubricate the sliding part of the compressor. Yes. For example, there is a piston type compression mechanism of the compressor, and the piston type compressor is formed with a cylinder for accommodating the piston. The piston type compressor performs a series of cycles in which the refrigerant is sucked in, compressed and discharged by the reciprocating motion of the piston. In this compressor, the lubricating oil is supplied together with the refrigerant to the inside of the piston and the cylinder, and then supplied to the crank chamber of the compressor, for example, from the gap between the piston and the cylinder, and lubricates the sliding portion of the drive mechanism. . Accordingly, since the amount of lubricating oil supplied to the compressor is affected by the flow rate of the refrigerant flowing through the compressor, depending on the operating state of the compressor, there is a risk of insufficient lubrication in the compressor, particularly in the crank chamber. Therefore, various techniques have been proposed to ensure a stable supply of lubricating oil.

  For example, in the cooling device of Patent Document 1, an accumulator is provided in the middle of the circuit in which the refrigerant circulates, that is, between the evaporator and the compressor. The accumulator separates a refrigerant containing lubricating oil into a vapor refrigerant, a liquid refrigerant, and a lubricating oil. The separated liquid is supplied from the accumulator to the suction pipe connected to the compressor by an ejector that uses a part of the high-pressure refrigerant discharged from the compressor, and is mixed with the vapor refrigerant in a gas state. Sent to the compressor. Therefore, since compression of liquid does not occur in the compressor, the compression efficiency is not impaired, and since the liquid refrigerant and lubricating oil are stably returned to the compressor by the ejector, these residual amounts are reduced in the refrigerant circulation circuit. In addition, it is possible to reduce the amount of refrigerant and lubricating oil used.

Moreover, in the compressor of patent document 2, the oil separation space is formed in the outer peripheral surface of a housing, and the refrigerant | coolant compressed by the compressor is discharged outside via an oil separation space. A bent oil separation passage is formed inside the oil separation space, and the refrigerant flowing through the oil separation passage collides with the wall of the passage, so that the lubricating oil is separated from the refrigerant. The separated lubricating oil moves to an oil return passage that connects the oil separation space and the crank chamber in the housing due to a pressure difference in the oil separation space, and is supplied to the crank chamber through this passage. Therefore, the compressor in Patent Document 2 reduces the amount of lubricating oil discharged to the outside together with the refrigerant, and ensures the amount of lubricating oil inside the compressor.
JP 2005-24163 A JP-A-10-196540

However, in Patent Document 1, the lubricating oil accumulated in the circuit through which the refrigerant circulates is returned to the suction portion of the compressor together with the refrigerant. For example, in a piston type compressor, the lubricating oil is returned to the suction chamber. Supplied in. Therefore, in order to supply the lubricating oil from the inside of the cylinder to the drive mechanism of the crank chamber of the compressor, a supply path for the lubricating oil from the inside of the cylinder to the crank chamber is secured by increasing the side clearance between the piston and the cylinder. . On the other hand, the enlargement of the side clearance increases the blow-by gas and causes a problem of reducing the performance of the compressor.
Further, in the compressor of Patent Document 2, the liquid lubricating oil accumulated in the bent oil separation passage moves in the oil separation passage to the oil return passage due to an internal pressure difference, and enters the crank chamber via the oil return passage. Have been supplied. Therefore, there is a problem that it is difficult to stably supply the accumulated lubricating oil to the crank chamber, and the supply of the lubricating oil is concentrated in a part of the crank chamber. There is also a problem that lubrication is difficult.

  The present invention has been made to solve such a problem, and provides a compressor lubrication system capable of ensuring a stable supply of lubricating oil to a compressor and solving a lack of lubrication in a crank chamber. The purpose is to do.

  In order to solve the above-described problem, a compressor lubrication system according to the present invention includes a crank chamber inside, a compressor that discharges after compressing refrigerant sucked from the outside, and a path that communicates with the compressor. A separator that separates a refrigerant containing lubricating oil into a gas and a liquid; a first ejector having a supply port, a discharge port, and a suction port that communicate with each other; and a supply port of the first ejector. A first path communicating with the discharge port, a second path communicating the discharge port of the first ejector with the crank chamber of the compressor, and a third path communicating the suction port of the first ejector with the separator The first ejector includes the first ejector when the refrigerant supplied from the compressor through the first path circulates from the supply port to the discharge port inside the first ejector. The negative pressure is generated inside the separator, the liquid of the separator is sucked from the suction port through the third path by the action of the negative pressure, and the mixture of the refrigerant and the liquid is discharged from the discharge port through the second path. It supplies to a crank chamber.

  The refrigerant containing lubricating oil is separated into gas and liquid by the separator, and the separated liquid contains lubricating oil. This lubricating oil is supplied to the crank chamber of the compressor by the ejector. Since the ejector operates using the high-temperature and high-pressure refrigerant discharged from the compressor, the lubricating oil is supplied from the separator to the crank chamber. Can be performed stably. Further, since the fluid in which the refrigerant and the lubricating oil are mixed by the ejector is injected in the form of a mist, the entire crank chamber can be uniformly lubricated.

  A second path that connects the discharge port of the first ejector to the crank chamber of the compressor, an on-off valve that opens and closes the second path, and a third path that connects the suction port of the first ejector to the separator In addition, a check valve for preventing flow in the direction from the suction port of the first ejector to the separator may be provided. Excessive amount of lubricating oil in the crank chamber generates heat due to fluid friction caused by shearing and stirring resistance, resulting in deterioration of lubricating performance and damage to seals. Further, this excessive amount of lubricating oil also causes power loss of the compressor. By opening and closing the on-off valve, the lubricating oil is supplied or stopped to the crank chamber of the compressor, and it is possible to prevent the lubricating oil from being excessively accumulated in the crank chamber. Also, when the load on the compressor is high, such as in idle operation or low-speed operation, and further when reducing the amount of lubricating oil in the refrigerant circuit in order to increase the cooling capacity, the lubricating oil is added to the crank chamber as necessary. Can be supplied.

  A second ejector separate from the first ejector, a fourth path communicating the supply port of the second ejector to the discharge port of the compressor, and a discharge port of the second ejector to the suction port of the compressor A fifth path that communicates, a sixth path that communicates the suction port of the second ejector to the crank chamber of the compressor, an on-off valve that opens and closes the fourth path to the fourth path, and a fifth path In addition, a check valve for preventing flow in the direction from the suction port of the compressor to the discharge port of the second ejector, an open / close valve for opening and closing the sixth path in the sixth path, and supply of the first ejector The first ejector is connected to the first path that communicates the port with the discharge port of the compressor, the on-off valve that opens and closes the first path, and the third path that communicates the suction port of the first ejector to the separator. And a check valve that prevents flow in the direction from the suction port to the separator Second ejector may be supplied a mixture of lubricating oil and refrigerant in the crank chamber portion to the suction port of the compressor. In addition to supplying the lubricating oil to the crank chamber of the compressor by the first ejector, the lubricating oil from the crank chamber is recovered by the second ejector, so that the amount of lubricating oil in the crank chamber can be easily adjusted. It is possible to perform reliably.

  A seventh path connecting the discharge port of the first ejector to the suction port of the compressor, an eighth path connecting the suction port of the first ejector to the crank chamber of the compressor, and a seventh path An on-off valve that opens and closes the path 7, an on-off valve that opens and closes the eighth path on the eighth path, and a first path that connects the supply port of the first ejector to the discharge port of the compressor, An on-off valve that opens and closes the first path, a second path that connects the discharge port of the first ejector to the crank chamber of the compressor, an on-off valve that opens and closes the second path, and a suction port of the first ejector A third path that communicates with the separator may include a check valve that prevents flow in the direction from the suction port of the first ejector to the separator. The single ejector can individually collect the lubricating oil from the crank chamber in addition to supplying the lubricating oil to the crank chamber of the compressor. Accordingly, since only one ejector needs to be mounted, the system mounting space can be reduced.

The separator may communicate with the discharge port of the compressor and separate the refrigerant discharged from the compressor into a gas and a liquid. By installing the separator in a position communicating with the discharge port of the compressor, that is, in the vicinity of the discharge port, the amount of lubricating oil contained in the refrigerant circulating in the cooling system can be reduced. Therefore, in the refrigerant circulating in the cooling system, the content of the lubricating oil that lowers the heat exchange rate of the refrigerant is reduced, so that it is possible to suppress the reduction in the heat exchange rate of the refrigerant.
The separator may communicate with the suction port of the compressor to separate the refrigerant before being sucked into the compressor into a gas and a liquid. By installing the separator at a position communicating with the suction port of the compressor, the liquid content in the refrigerant sucked into the compressor can be reduced. Therefore, it is possible to suppress a decrease in the compression efficiency of the compressor due to the liquid compression.

  According to the present invention, it is possible to secure a stable supply of lubricating oil to the compressor and to solve the lack of lubrication in the crank chamber.

Embodiments of the present invention will be described below with reference to the accompanying drawings.
Embodiment 1 FIG.
The compressor lubrication system 101 according to the first embodiment relates to a compressor constituting a cooling system for an air conditioner mounted on a vehicle and the lubrication system thereof.

First, as shown in FIG. 1, the air conditioner cooling system according to the first embodiment includes a compressor lubrication system 101 including a compressor 1 that compresses a refrigerant sucked from outside and discharges the refrigerant in a high temperature / high pressure state. A condenser 2 for cooling and liquefying the high-temperature and high-pressure refrigerant, an expansion valve 3 for expanding the high-pressure liquefied refrigerant, and an evaporator 4 for evaporating the low-temperature and low-pressure refrigerant are provided.
Further, a pipe 5 a that communicates the compressor lubrication system 101 with the condenser 2 is provided, and the pipe 5 a communicates with the discharge port 26 of the compressor 1. Next, a pipe 5 b for connecting the condenser 2 to the expansion valve 3 is provided, and a pipe 5 c for connecting the expansion valve 3 to the evaporator 4 is further provided. Further, a pipe 5 d that communicates the evaporator 4 with the compressor lubrication system 101 is provided, and the pipe 5 d communicates with the suction port 28 of the compressor 1. Therefore, the refrigerant discharged from the compressor 1 is returned to the compressor 1 again via the pipe 5a, the condenser 2, the pipe 5b, the expansion valve 3, the pipe 5c, the evaporator 4, and the pipe 5d in order.

Next, the configuration of the compressor lubrication system 101 according to the first embodiment is as follows.
As shown in FIG. 1, the compressor lubrication system 101 includes a compressor 1, an oil separator 41 that is a separator that separates a refrigerant into a gas and a liquid, an ejector 61 that is a first ejector, and a pipe that communicates them. It is constituted by.

Here, the structure of the compressor 1 is demonstrated based on FIG. The compressor 1 is a one-side swash plate type variable capacity compressor.
The compressor 1 includes a cylinder block 11 and is joined to a front housing 12 and a rear housing 13 at both ends thereof. A crank chamber 15 is formed by the inside of the front housing 12 and the cylinder block 11. Further, a drive shaft 16 penetrating the front housing 12 and penetrating into the cylinder block 11 is rotatably provided. The drive shaft 16 projects from the front housing 12 and is connected to an external drive source (not shown).

In the crank chamber 15, a swash plate 21 is provided on the drive shaft 16, and the swash plate 21 is provided to be inclined with respect to a plane perpendicular to the axis of the drive shaft 16 and its inclination angle can be changed. Further, the swash plate 21 rotates in synchronization with the drive shaft 16.
A plurality of cylindrical pistons 22 are connected to the swash plate 21, and the pistons 22 are arranged on a circumference around the drive shaft 16. The piston 22 is accommodated in a cylinder bore 11 a formed in the cylinder block 11, and reciprocates in the cylinder bore 11 a as the swash plate 21 rotates around the drive shaft 16.
A discharge chamber 25 is formed at the center of the rear housing 13, and a suction chamber 27 is formed in an annular shape so as to surround the outer periphery of the discharge chamber 25. The discharge chamber 25 is provided with a discharge port 26 communicating with an external cooling system, and further provided with a discharge port 30 communicating with each of the plurality of cylinder bores 11a. The discharge port 30 is provided with a discharge valve (not shown). It has been. The suction chamber 27 is provided with a suction port 28 that communicates with an external cooling system, and a suction port 29 that communicates with each of the plurality of cylinder bores 11a. The suction port 29 is provided with a suction valve (not shown). Yes.

Next, the ejector 61 will be described below.
As shown in FIG. 2, the ejector 61 has a supply port 61a, a discharge port 61b, and a suction port 61c on the outer peripheral surface thereof. The supply port 61a and the discharge port 61b are disposed on the same axis 61i and communicate with each other.
The path connecting the supply port 61a and the discharge port 61b decreases from the supply port 61a toward the discharge port 61b in the cross section area at the D portion 61d and minimizes the cross section area at the E portion 61e. The E portion 61e communicates with a substantially hollow conical space 61f. Further, the G portion 61g having a constant cross-sectional area larger than the E portion 61e communicates with the space 61f. The G portion 61g is followed by an H portion 61h. The H portion 61h increases its cross-sectional area toward the discharge port 61b and communicates with the discharge port 61b. The suction port 61c is provided perpendicular to the shaft 61i that connects the supply port 61a and the discharge port 61b, and communicates with the space 61f.

In the ejector 61, when the fluid is supplied from the supply port 61a, the supplied fluid is pressurized in the D part 61d and the E part 61e, discharged in a supersonic state in the space 61f, and sent to the G part 61g as it is. At this time, since a negative pressure is generated in the space 61f and a suction force is generated in the suction port 61c, fluid is sucked from the suction port 61c. The fluid supplied from the supply port 61a and the fluid sucked from the suction port 61c are mixed in the G part 61g, decelerated and pressurized in the H part 61h, and discharged from the discharge port 61b.
That is, the ejector 61 sucks fluid from the suction port 61c by the action of the fluid supplied to the supply port 61a, mixes and pressurizes these fluids, and discharges them.

  Returning to FIG. 1, the oil separator 41 is a cyclone type oil separator, and includes a suction port 41 a and an oil discharge port 41 b on the side, and a gas discharge port 41 c on the upper side. Further, inside the oil separator 41, a pipe 41d is connected to the gas outlet 41c, and the pipe 41d extends downward. Note that the pipe connected to the suction port 41a is arranged so that its central axis does not intersect the central axis of the pipe 41d. Therefore, when a refrigerant containing lubricating oil is supplied from the suction port 41a, the refrigerant generates a swirling flow around the pipe 41d inside the oil separator 41. At this time, the lubricating oil, which is liquid and has a high density, is pushed out by the outer edge of the swirling flow and separated from the refrigerant by centrifugal force. The lubricating oil separated from the refrigerant is stored at the bottom of the oil separator 41. Further, a pipe 41e is connected to the oil discharge port 41b, and the pipe 41e has an L shape, and a distal end that is a free end faces downward. The lubricating oil at the bottom of the oil separator 41 is discharged from the oil discharge port 41b through the pipe 41e.

In addition, a pipe 51 a that connects the discharge port 26 of the compressor 1 and the oil separator 41 is provided. The pipe 51 a has one end connected to the discharge port 26 and the other end connected to the suction port 41 a of the oil separator 41. Yes. Furthermore, a pipe 51 b is provided, one end of which is connected to the oil discharge port 41 b of the oil separator 41 and the other end of which is connected to the suction port 61 c of the ejector 61. Further, a pipe 51c having one end connected to the gas discharge port 41c of the oil separator 41 and the other end connected to the pipe 5a is provided. Furthermore, a pipe 51 d is provided in which one end is connected in the middle of the pipe 51 c and the other end is connected to the supply port 61 a of the ejector 61. Accordingly, a part of the pipes 51 a and 51 c, 51 d forms a first path that connects the discharge port 26 of the compressor and the supply port 61 a of the ejector 61, and the pipe 51 b is an oil discharge port 41 b of the oil separator 41. And a suction port 61c of the ejector 61 is formed as a third path.
The high-temperature and high-pressure refrigerant discharged from the discharge port 26 of the compressor 1 is supplied to the cooling system and the ejector 61 via the oil separator 41.

Further, a pipe 51 e is provided that has one end connected to the discharge port 61 b of the ejector 61 and the other end connected to the oil supply port 32 that communicates with the crank chamber 15 of the compressor 1. The pipe 51 e forms a second path that connects the discharge port 61 b of the ejector 61 and the crank chamber 15.
Further, a pipe 51f having one end connected to the suction port 28 of the compressor 1 and the other end connected to the pipe 5d is provided.

Next, the operation of the cooling system including the compressor lubrication system 101 according to the first embodiment will be described with reference to FIG.
The refrigerant is heated to a high temperature and a high pressure by the compressor 1 and then discharged in a gaseous state, and is sent to the condenser 2 through the pipes 51a, 51c and 5a. The high-temperature and high-pressure refrigerant sent to the condenser 2 is cooled and liquefied by the temperature difference from the outside air temperature in the condenser 2, but the liquefied refrigerant is in a high-pressure state.
This high-pressure liquefied refrigerant is sent to the expansion valve 3 via the pipe 5b, and is rapidly expanded by the expansion valve 3 to form a low-temperature / low-pressure mist. Note that the low-temperature and low-pressure refrigerant is easily vaporized.
Further, the low-temperature and low-pressure refrigerant is sent to the evaporator 4 through the pipe 5c, and the evaporator 4 absorbs heat from the ambient high-temperature air (air in the passenger compartment) and vaporizes it. That is, the air in the passenger compartment is cooled by the heat absorption effect of the refrigerant.
Further, the refrigerant evaporated in the evaporator 4 is sent again to the compressor 1 through the pipes 5d and 51f, and then brought to a high temperature and a high pressure, and thereafter the same process is performed.

Furthermore, the operation of the compressor 1 included in the compressor lubrication system 101 according to the first embodiment is as follows with reference to FIG.
When the drive shaft 16 is rotated by an external power source (not shown), the swash plate 21 is also rotated. By the rotation of the swash plate 21, the piston 22 reciprocates in the cylinder bore 11a. When the piston 22 slides from the top dead center toward the bottom dead center, a suction valve (not shown) is opened, and the refrigerant is sucked into the cylinder bore 11a from the pipe 51f through the suction chamber 27 and the suction port 29. Further, when the piston 22 reaches the bottom dead center and slides toward the top dead center, the suction port 29 is closed and the refrigerant in the cylinder bore 11a is compressed by the piston 22. The compressed refrigerant opens a discharge valve (not shown) and is discharged to the pipe 51 a through the discharge port 30 and the discharge chamber 25.
Further, by changing the inclination angle of the swash plate 21, the stroke amount of the piston 22 is changed, and the discharge capacity of the compressor 1 is changed. For example, when the swash plate 21 approaches perpendicular to the axis of the drive shaft 16, the drive shaft 16 and the swash plate 21 rotate, but the reciprocating motion of the piston 22 becomes extremely small, and the discharge capacity of the compressor 1 approaches 0%.

Therefore, the operation of the compressor lubrication system 101 according to the first embodiment is as follows with reference to FIG.
The refrigerant made high temperature and high pressure by the compressor 1 is supplied to the oil separator 41 through the pipe 51a in a state containing the lubricating oil. Although the refrigerant is separated into gas and liquid by the oil separator 41, the refrigerant supplied to the oil separator 41 is high temperature, so the separated liquid does not contain much refrigerant and contains a lot of lubricating oil and is separated. The gas contains a large amount of refrigerant. Further, the separated gaseous refrigerant is supplied from the gas outlet 41c of the oil separator 41 to the pipe 51c in a high temperature and high pressure state. A part of the high-temperature / high-pressure gaseous refrigerant supplied to the pipe 51c is supplied to the supply port 61a of the ejector 61 through the pipe 51d, and the other is circulated through the cooling system and compressed through the pipe 51f. Returned to the inlet 28 of the machine 1. On the other hand, the separated liquid lubricant is stored in the oil separator 41 and can be supplied from the oil discharge port 41b to the suction port 61c of the ejector 61 through the pipe 51b.

  When the high-temperature and high-pressure refrigerant supplied to the supply port 61a of the ejector 61 passes through the inside of the ejector 61, the lubricating oil of the oil separator 41 is sucked through the suction port 61c and the pipe 51b, and the supplied refrigerant and suction are sucked. The discharged lubricating oil is mixed and discharged from the discharge port 61b in a pressurized state. Furthermore, the mixed fluid of the discharged refrigerant and lubricating oil is sprayed into the crank chamber 15 through the pipe 51e and the oil supply port 32 of the compressor 1 in the form of a mist.

As described above, the compressor lubrication system 101 according to the first embodiment includes the compressor 1 including the crank chamber 15 therein, the oil separator 41, and the ejector 61.
The supply port 61 a of the ejector 61 communicates with the discharge port 26 of the compressor 1, the discharge port 61 b of the ejector 61 communicates with the crank chamber 15 of the compressor 1, and the suction port 61 c of the ejector 61 communicates with the oil separator 41.
The ejector 61 generates a negative pressure inside the ejector 61 when the refrigerant discharged from the discharge port 26 of the compressor 1 flows from the supply port 61a to the discharge port 61b inside the ejector 61, thereby generating a negative pressure. As a result, the lubricating oil separated from the refrigerant in the oil separator 41 is sucked from the suction port 61c, and the mixed fluid of the refrigerant and the lubricating oil is supplied to the crank chamber 15 through the discharge port 61b.

  With such a configuration of the compressor lubrication system 101, the ejector 61 operates using the high-temperature and high-pressure refrigerant discharged from the compressor 1, and the lubricating oil separated by the oil separator 41 is stabilized in the crank chamber 15. Can be supplied. Further, since the fluid mixture of the refrigerant and the lubricating oil is sprayed in the form of a mist by the ejector 61, the entire crank chamber 15 can be uniformly lubricated.

  Further, by installing the oil separator 41 at a position communicating with the discharge port 26 of the compressor 1, that is, in the vicinity of the discharge port 26, the amount of lubricating oil contained in the refrigerant circulating in the cooling system can be reduced. Accordingly, in the refrigerant circulating in the cooling system, the content of the lubricating oil that lowers the heat exchange rate of the refrigerant is reduced, so that the reduction in the heat exchange rate of the refrigerant can be suppressed and the cooling capacity can be improved.

Embodiment 2. FIG.
As shown in FIG. 3, the compressor lubrication system 102 according to the second embodiment is provided with an electromagnetic valve 71 that is an on-off valve for opening and closing the pipe 51e according to the first embodiment, and the pipe 51b receives oil from the ejector 61. A check valve 81 for preventing the flow to the separator 41 is provided. In the following embodiments, the same reference numerals as those in FIGS. 1 and 2 are the same or similar components, and thus detailed description thereof is omitted.
Other configurations are the same as those of the compressor lubrication system according to the first embodiment.

Referring to FIG. 3, in the operation of the compressor lubrication system 102 according to the second embodiment, the refrigerant discharged from the compressor 1 is supplied to the pipe 51 c through the oil separator 41. A part of the refrigerant supplied to the pipe 51c is supplied to the ejector 61 through the pipe 51d.
Here, when the electromagnetic valve 71 is opened, the lubricating oil of the oil separator 41 is supplied to the crank chamber 15 of the compressor 1 through the ejector 61 and the pipe 51e, as in the first embodiment. Lubricate the inside of the crank chamber 15.
Further, for example, when high-pressure discharge is required by the compressor 1 at a low vehicle speed, such as in an idling or low-speed driving state of the vehicle, that is, in a state where a high load is applied to the compressor 1, the crank chamber 15 In particular, the supply of lubricating oil is required, and the solenoid valve 71 is opened. Therefore, in the crank chamber 15, the electromagnetic valve 71 is opened not only when the operating condition of the compressor 1 that particularly requires the supply of the lubricating oil but also when the supply of the lubricating oil is required.

On the other hand, during normal operation, the electromagnetic valve 71 is closed. When the electromagnetic valve 71 is closed, the ejector 61 does not operate, and no lubricating oil is supplied to the crank chamber 15 of the compressor 1. Accordingly, the lubricating oil does not accumulate in the crank chamber 15 more than necessary. In addition, the refrigerant supplied to the ejector 61 tries to flow to the oil separator 41 through the pipe 51b, but this check is prevented by the check valve 81.
Other operations are the same as those of the compressor lubrication system according to the first embodiment.

  As described above, also in the compressor lubrication system 102 in the second embodiment, the same effect as in the first embodiment can be obtained.

Further, the excessive amount of lubricating oil stored in the crank chamber 15 increases power loss in the drive portion in the crank chamber 15, particularly when the compressor 1 is operating with a discharge capacity close to 0%. Let Further, the lubricating oil generates heat due to fluid friction and agitation due to shear, and the temperature of the lubricating oil rises. The increase in the lubricating oil temperature decreases the lubricating ability due to a decrease in the viscosity of the lubricating oil, and the seal performance of each part. By switching the supply or stop of supply of the lubricating oil to the crank chamber 15 by opening and closing the electromagnetic valve 71, the amount of the lubricating oil in the crank chamber 15 can be adjusted, and the above problem can be solved.
Further, when a high load is applied to the compressor during idle operation or low speed operation, the solenoid valve 71 is opened, so that the lubricating oil can be supplied to the crank chamber 15 as necessary. Furthermore, since the lubricating oil is stored in the crank chamber 15 by opening the electromagnetic valve 71, the amount of lubricating oil circulating in the cooling system can be reduced. Therefore, since the content of the lubricating oil that reduces the heat exchange rate of the refrigerant is reduced, the cooling capacity of the cooling system is improved. That is, when a high cooling capacity is required in the cooling system, the cooling capacity can be improved by opening the electromagnetic valve 71.

Embodiment 3 FIG.
As shown in FIG. 4, the compressor lubrication system 103 according to the third embodiment is provided with an accumulator 43 between the compressor 1 and the evaporator 4 instead of the oil separator 41 in the first embodiment. is there.
The configuration of the compressor lubrication system 103 according to Embodiment 3 is as follows with reference to FIG.
A pipe 53a having one end connected to the discharge port 26 of the compressor 1 and the other end connected to the pipe 5a is provided. Furthermore, a pipe 53 d is provided in which one end is connected in the middle of the pipe 53 a and the other end is connected to the supply port 61 a of the ejector 61. That is, the high-temperature and high-pressure refrigerant discharged from the discharge port 26 of the compressor 1 is supplied to the cooling system and the ejector 61 via the pipes 53a and 53d.

Next, as in the first embodiment, a pipe 51e that communicates the discharge port 61b of the ejector 61 and the crank chamber 15 of the compressor 1 is provided.
Further, a pipe 53f having one end connected to the suction port 28 of the compressor 1 and the other end connected to the pipe 5d is provided. An accumulator 43 is provided in the middle of the pipe 53f.
The accumulator 43 separates the sucked refrigerant into a gas and a liquid, and is a baffle type liquid separator. The accumulator 43 has a suction port 43a, a liquid discharge port 43b, and a gas discharge port 43c on the side. The suction port 43a communicates with the evaporator 4 via piping 53f and 5d, and the gas discharge port 43c communicates with the suction port 28 of the compressor 1 via piping 53f. Further, the liquid discharge port 43b of the accumulator 43 communicates with the suction port 61c of the ejector 61 through the pipe 53b. One end of the pipe 53b is connected to the liquid discharge port 43b and the other end is connected to the suction port 61c of the ejector 61. ing.

  In the accumulator 43, a pipe 43d is connected to the suction port 43a, and a pipe 43e is connected to the liquid discharge port 43b. Each of the pipes 43d and 43e has an L-shape, and the tip which is a free end faces downward. Furthermore, a pipe 43f is connected to the gas outlet 43c. The pipe 43f has an L shape, and the tip which is a free end faces upward. A plurality of baffle plates 43g surrounding the pipe 43d are provided in the vertical portion of the pipe 43d. The baffle plate 43g has a conical shape that spreads downward, and is provided with a large number of small holes that penetrate the baffle plate 43g.

When a refrigerant containing lubricating oil is supplied from the suction port 43 a of the accumulator 43, the refrigerant discharged from the pipe 43 d flows upward in the accumulator 43. Since the flow rate of the refrigerant is reduced by the baffle plate 43g, the liquid refrigerant and the lubricating oil contained in the refrigerant are separated by gravity. Further, the refrigerant collides with the baffle plate 43g and changes its moving direction, so that the liquid refrigerant and lubricating oil contained therein are separated. The separated liquid refrigerant and lubricating oil accumulate at the bottom of the accumulator 43 and are discharged from the liquid discharge port 43b through the pipe 43e. Note that the gaseous refrigerant separated in the accumulator 43 is discharged from the gas discharge port 43c through the pipe 43f.
Other configurations are the same as those of the compressor lubrication system according to the first embodiment.

Next, the operation of the compressor lubrication system 103 according to Embodiment 3 is as follows.
Referring to FIG. 4, the refrigerant that has been brought to a high temperature and a high pressure by compressor 1 is supplied to the cooling system via piping 53a in a state containing lubricating oil. The refrigerant circulated through the cooling system is supplied to an accumulator 43 provided in the middle thereof through a pipe 53f, and is separated into a gaseous refrigerant, a liquid refrigerant, and lubricating oil by the accumulator 43.
Further, the separated gaseous refrigerant is supplied to the suction port 28 of the compressor 1, and the separated liquid refrigerant and lubricating oil are stored in the accumulator 43.

A part of the high-temperature and high-pressure refrigerant supplied to the pipe 53a is supplied to the supply port 61a of the ejector 61 through the pipe 53d. Therefore, the ejector 61 sucks the liquid refrigerant and lubricating oil stored in the accumulator 43 from the suction port 61c, mixes it with the refrigerant supplied to the supply port 61a, boosts the pressure, and then discharges it from the discharge port 61b. Further, the mixed fluid is sprayed into the crank chamber 15 through the pipe 51e.
Other operations are the same as those of the compressor lubrication system according to the first embodiment.

Thus, also in the compressor lubrication system 103 according to the third embodiment, the same effect as in the first embodiment can be obtained.
Further, the liquid contained in the refrigerant sucked into the compressor 1 is removed by the accumulator 43, so that the compressor 1 can suppress a decrease in the compression efficiency of the refrigerant due to the compression of the liquid.
In the third embodiment, the refrigerant containing the lubricating oil is separated into the gaseous refrigerant, the liquid refrigerant, and the lubricating oil by the accumulator 43. However, the lubricating oil separator is provided separately from the accumulator 43, and Lubricating oil separated from the refrigerant may be sent to the accumulator 43.

Embodiment 4 FIG.
As shown in FIG. 5, the compressor lubrication system 104 according to the fourth embodiment is provided with an ejector 62 that is a second ejector in the compressor lubrication system according to the first embodiment. The ejector 62 collects lubricating oil in the crank chamber 15 of the compressor 1 by its action, and supplies the lubricating oil to the suction port 28 of the compressor 1.

The configuration of the compressor lubrication system 104 according to the fourth embodiment is as follows with reference to FIG.
First, in the compressor lubrication system 104 according to the fourth embodiment, in addition to the compressor lubrication system according to the first embodiment, a check valve 82 for preventing the flow from the ejector 61 to the oil separator 41 is provided in the pipe 51b. Is provided. An electromagnetic valve 72 that opens and closes the pipe 51d is provided in the middle of the pipe 51d that connects the pipe 51c and the ejector 61.
Next, a pipe 54g having one end connected in the middle of the pipe 51d and the other end connected to the supply port 62a of the ejector 62 is provided. The pipe 54g is connected to the pipe 51d between the connection part of the pipes 51c and 51d and the solenoid valve 72. Accordingly, a part of the pipes 51a and 51c, a part of 51d, and 54g form a fourth path that connects the discharge port 26 of the compressor 1 and the supply port 62a of the ejector 62. Further, an electromagnetic valve 73 for opening and closing the pipe is provided in the middle of the pipe 54g.

In addition, a pipe 54h is provided with one end connected to the discharge port 62b of the ejector 62 and the other end connected in the middle of the pipe 51f. Accordingly, a part of the pipes 54 h and 51 f forms a fifth path that connects the discharge port 62 b of the ejector 62 and the suction port 28 of the compressor 1. Further, a check valve 83 for preventing the flow from the pipe 51f to the discharge port 62b of the ejector 62 is provided in the middle of the pipe 54h.
Further, a pipe 54 i is provided that has one end connected to the suction port 62 c of the ejector 62 and the other end connected to the oil recovery port 33 that communicates with the crank chamber 15 of the compressor 1. That is, the pipe 54 i forms a sixth path that connects the suction port 62 c of the ejector 62 and the crank chamber 15. Further, an electromagnetic valve 74 for opening and closing the pipe is provided in the middle of the pipe 54i.
Other configurations are the same as those of the compressor lubrication system according to the first embodiment.

Next, the operation of the compressor lubrication system 104 according to the fourth embodiment is as follows.
Referring to FIG. 5, the high-temperature / high-pressure refrigerant discharged from compressor 1 is supplied to piping 51c via oil separator 41 and further supplied to the cooling system. A part of the refrigerant gas supplied to the pipe 51c is supplied to the pipe 51d.

When the solenoid valve 72 is opened, the refrigerant supplied to the pipe 51d is supplied to the supply port 61a of the ejector 61, and the supplied refrigerant and the lubricating oil of the oil separator 41 are the same as in the first embodiment. Are mixed and sprayed into the crank chamber 15 of the compressor 1. At this time, the electromagnetic valve 74 provided in the pipe 54i is closed, and the lubricating oil in the crank chamber 15 is prevented from flowing out of the crank chamber 15 through the pipe 54i.
Here, when the electromagnetic valve 72 is closed, the ejector 61 stops and the supply of the lubricating oil to the crank chamber 15 is stopped. At this time, when the internal pressure of the crank chamber 15 is larger than the internal pressure of the oil separator 41, there is a possibility that the lubricating oil in the crank chamber 15 flows back to the oil separator 41 via the ejector 61, but the reverse provided in the pipe 51b. This back flow is prevented by the stop valve 82.
Therefore, the lubricating oil is supplied to the crank chamber 15 by opening the electromagnetic valve 72, and the supply of the lubricating oil is stopped by closing the valve.

Further, when the electromagnetic valve 73 is opened, the high-temperature and high-pressure refrigerant is supplied to the supply port 62a of the ejector 62 through the pipe 54g. At this time, the solenoid valve 74 of the pipe 54i is opened. By the action of the ejector 62, the lubricating oil in the crank chamber 15 is sucked into the ejector 62 through the pipe 54i, and is discharged from the discharge port 62b in a state of being mixed and pressurized with the supplied refrigerant. The fluid mixture of the discharged refrigerant and lubricating oil is supplied to the pipe 51f through the pipe 54h, mixed with the refrigerant circulating in the cooling system, and supplied to the suction port 28 of the compressor 1.
Here, when the electromagnetic valve 73 is closed, the ejector 62 stops and the recovery of the lubricating oil in the crank chamber 15 is stopped. At this time, the refrigerant in the pipe 51 f may flow into the crank chamber 15 through the ejector 62 and further through the pipe 54 i through the pipe 54 h, but this inflow is prevented by the check valve 83. Further, the solenoid valve 74 provided in the pipe 54 i is closed, and the lubricating oil in the crank chamber 15 is prevented from flowing out of the crank chamber 15.
Therefore, the lubricating oil in the crank chamber 15 is recovered by opening the electromagnetic valve 73, and the recovery of the lubricating oil is stopped by closing the valve.

Accordingly, when the solenoid valve 72 is opened and the solenoid valves 73 and 74 are closed, lubricating oil is supplied to the crank chamber 15, the solenoid valve 72 is closed, and the solenoid valves 73 and 74 are opened. As a result, the lubricating oil is recovered from the crank chamber 15. Further, when the solenoid valves 72, 73, 74 are closed, the lubricating oil is not supplied to or recovered from the crank chamber 15.
In other words, the supply and recovery of the lubricating oil to the crank chamber 15 are performed individually by opening and closing operations of the electromagnetic valves 72, 73, 74, and the amount of lubricating oil in the crank chamber 15 is adjusted.
Other operations are the same as those of the compressor lubrication system according to the first embodiment.

Thus, also in the compressor lubrication system 104 in Embodiment 4, the effect similar to the said Embodiment 1 is acquired.
In addition to supplying the lubricant oil to the crank chamber 15 of the compressor 1 by the ejector 61, the lubricant oil in the crank chamber 15 can be individually recovered by the ejector 62. Therefore, the same effects as those of the second embodiment can be obtained, and the amount of lubricating oil in the crank chamber 15 can be adjusted easily and reliably.

Embodiment 5 FIG.
The compressor lubrication system 105 according to the fifth embodiment supplies only one ejector 61 to supply the lubricant to the crank chamber 15 or collect the lubricant from the crank chamber 15 in the compressor lubrication system according to the fourth embodiment. It is what you use.
As shown in FIG. 6, the configuration of the compressor lubrication system 105 according to the fifth embodiment is as follows.
First, in addition to the compressor lubrication system according to the first embodiment, the compressor lubrication system 105 according to the fifth embodiment includes a check valve 84 that prevents the flow from the ejector 61 to the oil separator 41 in the pipe 51b. Is provided. Furthermore, the solenoid valves 75 and 76 which open and close these piping are provided in piping 51d and 51e, respectively.

Next, a pipe 55j that communicates the pipe 51e and the suction port 28 of the compressor 1 is provided. One end of the pipe 55j is connected to the pipe 51e between the discharge port 61b of the ejector 61 and the solenoid valve 76, and the other end is connected to the middle of the pipe 51f. Accordingly, a part of the pipe 51e and a part of 55j, 51f form a seventh path that connects the discharge port 61b of the ejector 61 and the suction port 28 of the compressor 1. Further, an electromagnetic valve 77 for opening and closing the pipe is provided in the middle of the pipe 55j.
Further, a pipe 55k is provided that communicates between the crank chamber 15 of the compressor 1 and the suction port 61c of the ejector 61. One end of the pipe 55k is connected to the oil recovery port 33 communicating with the crank chamber 15, and the other end is connected to the pipe 51b between the check valve 84 and the suction port 61c. Accordingly, a part of the pipe 51b and 55k form an eighth path that connects the suction port 61c and the crank chamber 15 of the compressor. Further, an electromagnetic valve 78 for opening and closing the pipe is provided in the middle of the pipe 55k.
Other configurations are the same as those of the compressor lubrication system according to the first embodiment.

Next, the operation of the compressor lubrication system according to Embodiment 5 is as follows.
As shown in FIG. 6, the ejector 61 operates when the electromagnetic valve 75 provided in the pipe 51d is opened, and stops when the electromagnetic valve 75 is closed.

  When lubricating oil is supplied to the crank chamber 15, the electromagnetic valve 75 is opened to operate the ejector 61. The ejector 61 sucks the lubricating oil of the oil separator 41 from the suction port 61c through the pipe 51b, and pressurizes and discharges the mixed fluid of the refrigerant and the lubricating oil from the discharge port 61b. The discharged mixed fluid is piped It is supplied to the crank chamber 15 via 51e. At this time, the electromagnetic valve 76 provided in the pipe 51e is opened. In addition, the electromagnetic valve 77 is closed to prevent the mixed fluid discharged from the discharge port 61b from flowing out through the pipe 55j. Further, the solenoid valve 78 is closed to prevent the lubricating oil in the crank chamber 15 from being sucked into the suction port 61c through the pipe 55k by the action of the ejector 61.

  Next, even when the lubricating oil in the crank chamber 15 is recovered, the electromagnetic valve 75 is opened to operate the ejector 61. Further, the electromagnetic valve 78 provided in the pipe 55k is opened. At this time, the ejector 61 sucks the lubricating oil in the crank chamber 15 from the suction port 61c through the pipe 55k, and boosts and discharges the mixed fluid of the refrigerant and the lubricating oil from the discharge port 61b. In the suction port 61c, the lubricating oil of the oil separator 41 is also sucked through the pipe 51b, and is mixed with the lubricating oil and discharged from the discharge port 61b. The discharged mixed fluid is supplied to the pipe 51f through the pipes 51e and 55j, mixed with the refrigerant in the pipe 51f, and supplied to the suction port 28 of the compressor 1. Note that the solenoid valve 77 is opened so that the mixed fluid discharged from the discharge port 61b flows into the pipe 51f via the pipe 55j. Further, the electromagnetic valve 76 is closed to prevent the mixed fluid from flowing into the crank chamber 15 via the pipe 51e.

  Further, when it is not necessary to supply the lubricating oil to the crank chamber 15 and it is not necessary to collect the lubricating oil in the crank chamber 15, the electromagnetic valve 75 is closed and the ejector 61 does not operate. Further, the electromagnetic valves 76 and 78 are closed, the pipes 51e and 55k communicating with the crank chamber 15 are closed, and the flow to the crank chamber 15 is shut off.

Accordingly, the solenoid valves 75 and 76 are opened, and the solenoid valves 77 and 78 are closed, whereby lubricating oil is supplied to the crank chamber 15. Further, the solenoid valves 75, 77 and 78 are opened, and the solenoid valve 76 is closed, whereby the lubricating oil is recovered from the crank chamber 15. Further, when the solenoid valves 75, 76, 78 are closed, no lubricating oil is supplied to or recovered from the crank chamber 15.
Other operations are the same as those of the compressor lubrication system according to the first embodiment.

Thus, also in the compressor lubrication system 105 in Embodiment 5, the effect similar to the said Embodiment 1 is acquired.
In addition to supplying the lubricating oil to the crank chamber 15 of the compressor 1, the lubricating oil can be collected individually, so that the same effect as that of the fourth embodiment can be obtained. Oil can be supplied and recovered by a single ejector 61. Therefore, in the fifth embodiment, one solenoid valve is added and one check valve is reduced to the compressor lubrication system according to the fourth embodiment, but the number of ejectors is reduced from two to one. Therefore, the system mounting space can be reduced.

  In the first, second, fourth, and fifth embodiments, the discharge port 26 of the compressor 1 and the supply port 61a of the ejector 61 communicate with each other via the oil separator 41, but the present invention is not limited to this. It is only necessary that the high-temperature and high-pressure refrigerant discharged from the compressor 1 is supplied to the supply port 61a. For example, the discharge port 26 and the supply port 61a may directly communicate with each other without using the oil separator 41. That is, a pipe that directly communicates the discharge port 26 and the supply port 61a may be provided separately, and this pipe may be branched from the pipe 51a and connected to the supply port 61a.

In the first, second, fourth, and fifth embodiments, the separator is the oil separator 41. However, the separator is not limited to this, and may be built in the compressor 1, for example, a discharge port. 26 may be a discharge muffler communicating with H.26. At this time, the lubricating oil collected at the corner of the discharge muffler may be sucked by the ejector 61.
In the first, second, fourth, and fifth embodiments, the oil separator 41 is a cyclone type, but is not limited to this, and may be a baffle type, a wire net type, a demister type, or the like.
In the third embodiment, the accumulator 43 is a baffle type, but is not limited thereto, and may be a double barrel type.

It is a figure which shows the structure of the cooling system containing the compressor lubrication system which concerns on Embodiment 1 of this invention. It is a cross-sectional side view of the ejector of FIG. It is a figure which shows the structure of the cooling system containing the compressor lubrication system which concerns on Embodiment 2 of this invention. It is a figure which shows the structure of the cooling system containing the compressor lubrication system which concerns on Embodiment 3 of this invention. It is a figure which shows the structure of the cooling system containing the compressor lubrication system which concerns on Embodiment 4 of this invention. It is a figure which shows the structure of the cooling system containing the compressor lubrication system which concerns on Embodiment 5 of this invention.

Explanation of symbols

  1 compressor, 15 crank chamber, 26 discharge port, 28 suction port, 41 oil separator (separator), 43 accumulator (separator), 51a, 51c, 51d, 53a, 53d piping (first path), 51b, 53b pipe (third path), 51e pipe (second path), 54g pipe (fourth path), 54h pipe (fifth path), 54i pipe (sixth path), 55j pipe (seventh path) ), 55k pipe (eighth path), 61 ejector (first ejector), 61a, 62a supply port, 61b, 62b discharge port, 61c, 62c suction port, 62 ejector (second ejector), 71 , 72, 73, 74, 75, 76, 77, 78 Solenoid valve (open / close valve), 81, 82, 83, 84 Check valve, 101, 102, 103, 104, 1 5 compressor lubrication system.

Claims (6)

A compressor having a crank chamber inside and compressing refrigerant sucked from the outside and then discharging;
A separator provided in a path communicating with the compressor, and separating a refrigerant containing lubricating oil into a gas and a liquid;
A first ejector having a supply port, a discharge port and a suction port in communication with each other;
A first path communicating the supply port of the first ejector with a discharge port of the compressor;
A second path communicating the discharge port of the first ejector with the crank chamber of the compressor;
A third path communicating the suction port of the first ejector to the separator;
The first ejector is configured such that when the refrigerant supplied from the compressor through the first path flows from the supply port toward the discharge port in the first ejector, the first ejector A negative pressure is generated inside one ejector, and the liquid of the separator is sucked from the suction port through the third path by the action of the negative pressure, and the mixture of the refrigerant and the liquid is discharged. A compressor lubrication system, wherein the crank chamber is supplied from a port through the second path. An on-off valve for opening and closing the second path in the second path communicating the discharge port of the first ejector with the crank chamber of the compressor;
A check valve for preventing flow in the direction from the suction port of the first ejector to the separator is provided in the third path communicating the suction port of the first ejector with the separator. The compressor lubrication system according to claim 1. A second ejector separate from the first ejector;
A fourth path communicating the supply port of the second ejector with the discharge port of the compressor;
A fifth path communicating the discharge port of the second ejector with the suction port of the compressor;
A sixth path communicating the suction port of the second ejector with the crank chamber of the compressor;
An on-off valve for opening and closing the fourth path in the fourth path;
A check valve for preventing flow in the direction from the suction port of the compressor to the discharge port of the second ejector in the fifth path;
An on-off valve for opening and closing the sixth path to the sixth path;
An on-off valve for opening and closing the first path in the first path communicating the supply port of the first ejector with the discharge port of the compressor;
A check valve for preventing flow in the direction from the suction port of the first ejector to the separator in the third path communicating the suction port of the first ejector with the separator; ,
2. The compressor lubrication system according to claim 1, wherein the second ejector supplies a mixture of the lubricating oil and the refrigerant in the crank chamber to the suction port of the compressor. A seventh path communicating the discharge port of the first ejector with the suction port of the compressor;
An eighth path communicating the suction port of the first ejector with the crank chamber of the compressor;
An on-off valve for opening and closing the seventh path in the seventh path;
An on-off valve for opening and closing the eighth path to the eighth path;
An open / close valve that opens and closes the first path to a first path communicating the supply port of the first ejector with the discharge port of the compressor;
An on-off valve that opens and closes the second path to a second path communicating the discharge port of the first ejector with the crank chamber of the compressor;
A check valve for preventing flow in the direction from the suction port of the first ejector to the separator is provided in a third path communicating the suction port of the first ejector with the separator. The compressor lubrication system according to claim 1.   5. The separator according to claim 1, wherein the separator communicates with the discharge port of the compressor and separates the refrigerant discharged from the compressor into a gas and a liquid. The compressor lubrication system described.   5. The separator according to claim 1, wherein the separator communicates with an inlet of the compressor and separates the refrigerant before being sucked into the compressor into a gas and a liquid. Compressor lubrication system as described in.

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