JP6655366B2 - Compressor - Google Patents

Description

  The technology disclosed herein relates to a compressor.

  As a compressor suitable for compressing a refrigerant or the like, a compressor configured to relieve lubricating oil discharged from an oil supply pump in accordance with the discharge pressure is known.

  For example, Patent Literature 1 discloses a casing (sealed housing) through which a gas flows, a compression mechanism housed in the casing and configured to compress the gas, and sucks up a lubricating oil forming an oil reservoir in the casing. An oil supply pump for supplying the lubricating oil to a compression mechanism through a discharge passage (oil supply hole); and, when the discharge pressure of the lubricating oil is equal to or higher than a predetermined pressure, the lubricating oil is stored in an oil sump to prevent excessive lubrication. There is disclosed a compressor having a relief valve for relief (releasing).

JP-A-04-214993

  However, in the configuration of Patent Literature 1, the relief lubricating oil may scatter in the casing, or the scattered lubricating oil may agitate the oil reservoir. In that case, the amount of oil floating as droplets in the casing increases, which may lead to an increase in the amount of oil flowing out of the casing along with the flow of gas, and consequently poor lubrication of the compression mechanism.

  In particular, when the above-described compressor is applied to a refrigeration cycle, the efficiency of the refrigeration cycle may be degraded by increasing the amount of oil rise as described above.

  The technology disclosed herein is made in view of such a point, and an object thereof is to provide a compressor configured to relieve lubricating oil discharged from an oil supply pump in accordance with the discharge pressure. Another object is to prevent poor lubrication of the compression mechanism.

  The technology disclosed herein relates to a compressor. The compressor includes a casing through which a gas flows, a compression mechanism housed in the casing and configured to compress the gas, an oil supply pump, and a lubricating oil forming an oil sump in the casing. An oil supply mechanism having a suction passage leading to an oil supply pump and a discharge passage leading to the compression mechanism the lubricating oil discharged from the oil supply pump, wherein the oil supply mechanism has a discharge pressure of the lubricating oil of a predetermined pressure or more. Sometimes, the lubricating oil is configured to be relieved from the discharge passage into the suction passage.

  According to this configuration, the relieved lubricating oil scatters not into the casing but into the suction passage. Since the lubricating oil scattered in the suction passage floats as a droplet in the suction passage, it is isolated from the gas flow flowing through the casing. Further, by scattering the oil in the suction passage, the agitation of the oil pool by the relieved lubricating oil is suppressed. Therefore, the amount of oil floating as splashes in the casing and the amount of oil flowing out of the casing along with the flow of gas are reduced.

  Thus, according to the above configuration, it is possible to prevent poor lubrication of the compression mechanism.

  In particular, when the compressor is applied to a refrigeration cycle, it is possible to prevent the efficiency of the refrigeration cycle from deteriorating by reducing the oil rise as described above.

  In addition, preventing poor lubrication of the compression mechanism is advantageous in increasing the rotation speed of the compression mechanism and, in turn, reducing the size of the compressor. 2. Description of the Related Art Hitherto, as one of measures for realizing downsizing of a compressor, increasing the rotation speed of a compression mechanism has been considered. Generally, a large amount of lubricating oil is relieved in a high rotation range, so that the problem of poor lubrication caused by the lubricating oil relief as described above may become more serious. Therefore, the configuration described above is effective in realizing a high rotation speed of the compression mechanism and a reduction in the size of the compressor in that lubricating oil can be prevented from poor lubrication due to the relief of lubricating oil.

  The suction passage may be provided with a storage chamber in which a second oil reservoir is formed, and the oil supply mechanism may be configured to relieve the lubricating oil into the storage chamber.

  According to this configuration, the relieved lubricating oil scatters into the storage chamber, and forms a second oil sump in the storage chamber. As described above, since the relieved lubricating oil is stored in the storage chamber, it is possible to reduce the amount of oil returning to the oil sump via the suction passage. This is advantageous in suppressing the agitation of the oil sump by the relieved lubricating oil, and thereby preventing poor lubrication of the compression mechanism.

  Furthermore, according to the above configuration, the relieved lubricating oil is isolated from the gas flow flowing through the casing because it is isolated in the storage chamber. Therefore, it is advantageous in reducing the amount of oil flowing out of the casing along with the flow of gas, and thereby preventing poor lubrication of the compression mechanism.

  Further, the oil supply mechanism includes a relief port that communicates the discharge passage with the suction passage, and a relief valve that opens and closes the relief port in accordance with a discharge pressure of the lubricating oil. It may be arranged in the storage room.

  According to this configuration, the provision of the storage chamber in the middle of the suction passage is effective in securing a space for disposing the relief valve in the suction passage.

  Further, the refueling pump may be a positive displacement pump.

  A rotating shaft connected to the motor and driving the compression mechanism and the oil supply mechanism; and a rotating shaft extending in an axial direction of the rotating shaft inside the rotating shaft. An oil supply hole may be formed, and the oil supply hole may constitute the discharge passage.

  Further, the casing may be arranged so that an axial direction of the rotating shaft is along a horizontal direction.

  As described above, according to the compressor described above, the amount of oil floating as splashes in the casing and the amount of oil flowing out of the casing by flowing the gas flow by relieving the lubricating oil into the suction passage. Is reduced, it is possible to prevent poor lubrication of the compression mechanism, and in particular, it is possible to prevent the efficiency of the refrigeration cycle from deteriorating.

It is a longitudinal section of a compressor. It is a longitudinal cross-sectional view which expands and shows the structure near a refueling pump. It is a cross-sectional view schematically showing a configuration of a refueling pump. It is a graph which shows the oil discharge amount of lubricating oil.

  Hereinafter, the compressor will be described with reference to the drawings. Note that the description of the following embodiment is an exemplification. FIG. 1 shows the compressor 10, and FIG. 2 shows an enlarged view of a configuration near a refueling pump 51 of a refueling mechanism 50 constituting the compressor 10. The compressor 10 according to this embodiment is connected to a refrigerant circuit of a refrigeration apparatus (not shown). In this refrigerating apparatus, the gas refrigerant compressed by the compressor 10 becomes a liquid refrigerant by radiating heat in a condenser (radiator) and is decompressed by a decompression mechanism. The decompressed liquid refrigerant evaporates in the evaporator to become a gas refrigerant again, and is sucked into the compressor 10. That is, in the refrigerant circuit of the refrigeration apparatus, the refrigerant circulates to perform a vapor compression refrigeration cycle. Note that the gas refrigerant is an example of “gas”.

  First, the overall configuration of the compressor 10 will be described.

  As shown in FIG. 1, the compressor 10 includes a casing 11 through which a gas refrigerant flows, an electric motor 20 accommodated in the casing 11, a rotating shaft 30 connected to the motor 20, and a casing 11 accommodated in the casing 11. , A compression mechanism 40 and an oil supply mechanism 50 driven by the rotating shaft 30.

  The casing 11 is formed of a cylindrical closed container having both ends closed. As shown in FIG. 1, the casing 11 is arranged such that the axial direction of the rotating shaft 30 (hereinafter, simply referred to as “axial direction”) extends along the horizontal direction, in other words, the rotating axis X of the rotating shaft 30. Are arranged parallel to the horizontal direction. That is, the compressor 10 according to this embodiment is configured as a so-called horizontal compressor.

  Further, a suction pipe 12 connected to the evaporator and a discharge pipe 13 connected to the condenser are connected to the casing 11 in an airtight manner, and the gas refrigerant flows through the suction pipe 12 into the casing 11. And flows out of the casing 11 through the discharge pipe 13. The suction pipe 12 penetrates a side surface near one end of the casing 11 in the radial direction of the rotating shaft 30 (hereinafter, simply referred to as “radial direction”), while the discharge pipe 13 has the other end face of the casing 11 Penetrating in the direction.

  In the following description, of the directions along the axial direction, a direction from one end (the suction pipe 12 side) to the other end (the discharge pipe 13 side) of the casing 11 is referred to as a rear direction, and the other end faces the one end. The direction is the forward direction.

  The motor 20 has a stator 21 fixed to the inner peripheral wall of the casing 11 and a rotor 22 inserted inside the stator 21, and a rotating shaft 30 is fixed to the center of the rotor 22. .

  As described above, the rotary shaft 30 is disposed along the horizontal direction, and an oil supply hole 30a that penetrates the rotary shaft 30 in the axial direction is formed therein. A compression mechanism 40 is connected to the front end side of the rotating shaft 30, and a front end face of the oil supply hole 30 a is opened into the compression mechanism 40. On the other hand, an oil supply mechanism 50 is connected to the rear end side of the rotary shaft 30, and the rear end of the oil supply hole 30 a is inserted into an oil supply pump 51 of the oil supply mechanism 50 through an upstream oil supply hole 33 a described later. Communicating. Further, a plurality of through holes 30 b penetrating through the peripheral wall portion in the radial direction are formed in the peripheral wall portion of the rotating shaft 30. The through holes 30b are arranged at intervals in the axial direction, and open to the vicinity of a pump bearing member 31, a scroll housing 41, and a scroll bearing member 42b, which will be described later.

  The compression mechanism 40 is a so-called scroll-type compression mechanism, and includes a scroll housing 41, a movable scroll 42, and a fixed scroll 43.

  The scroll housing 41 is formed in a substantially disk shape, and is fixed to the inner peripheral surface of the casing 11. The scroll housing 41 rotatably supports a front portion of the rotary shaft 30. The front end of the rotary shaft 30 penetrates the scroll housing 41 and is eccentric in the radial direction by a predetermined amount with respect to the rotation axis X of the rotary shaft 30.

  The movable scroll 42 is formed in a disk shape smaller in diameter than the inner diameter of the casing 11, and a movable side wrap 42a formed in a spiral shape is provided upright on the front surface thereof. On the other hand, a tubular scroll bearing member 42b is provided upright on the rear surface of the movable scroll 42, and the front end of the rotary shaft 30 is inserted therein. When the rotation shaft 30 rotates, the orbiting scroll 42 revolves around the rotation axis X of the rotation shaft 30. In addition, the orbiting motion of the orbiting scroll 42 is prevented by a member (not shown) such as an Oldham coupling at the time of orbit.

  The fixed scroll 43 is formed in a bottomed cylindrical shape with an open rear surface, and is fixed to the inner peripheral surface of the casing 11. On the inner bottom surface of the fixed scroll 43, a fixed side wrap 43a formed in a spiral shape is provided upright. Further, a through hole 43b is provided on the outer peripheral surface of the fixed scroll 43 so as to penetrate the outer peripheral surface in the radial direction. The suction pipe 12 is connected to the through hole 43b.

  In the compression mechanism 40, a plurality of compression chambers C for compressing gas refrigerant are partitioned between the movable scroll 42 and the fixed scroll 43 by radially meshing the movable wrap 42a and the fixed wrap 43a. Have been. The compression chamber C communicates with the suction pipe 12 through the above-described through hole 43b, and is configured to compress the gas refrigerant flowing from the suction pipe 12 when the movable scroll 42 revolves.

  The gas refrigerant compressed by the compression mechanism 40 fills a space on the rear side of the scroll housing 41 in the casing 11 and flows out of the discharge pipe 13 through a discharge passage (not shown). The lubricating oil contained in the gas refrigerant is stored in this space, and forms an oil reservoir S1 at the inner bottom of the casing 11, as shown in FIG. As described above, since the compressor 10 is configured as a horizontal compressor, the oil level of the oil sump S1 extends parallel to the axial direction.

  A pump bearing member 31 that rotatably supports a rear portion of the rotating shaft 30 is provided at a rear portion in the casing 11. The pump bearing member 31 is formed in a cylindrical shape extending in the front-back direction, and is fixed to the inner peripheral surface of the casing 11 via a stay 32 formed in a disk shape. The stay 32 has a flow hole (not shown) penetrating the stay 32 in the axial direction. The lubricating oil flows through the holes.

  The above-described oil supply hole 30a is opened at the rear end surface of the rotary shaft 30, and a pump drive shaft 33 is inserted into the oil supply hole 30a.

  The pump drive shaft 33 is formed in a cylindrical shape extending coaxially with the rotary shaft 30, and is configured to rotate integrally with the rotary shaft 30. The pump drive shaft 33 is formed with an upstream oil supply hole 33 a penetrating the pump drive shaft 33 in the axial direction. The upstream oil supply hole 33a communicates with the oil supply hole 30a of the rotary shaft 30.

  The compressor 10 according to this embodiment sucks up lubricating oil from the oil sump S1, and supplies the lubricating oil to the pump bearing member 31, the scroll housing 41, the scroll bearing member 42b, the rotating shaft 30, the compression mechanism 40, and the like. And a refueling mechanism 50 configured to perform the above operation.

  Hereinafter, the configuration of the refueling mechanism 50 will be described in detail.

  As shown in FIG. 2, the oil supply mechanism 50 includes an oil supply pump 51, a suction passage 52 that guides the lubricating oil forming the oil reservoir S <b> 1 to the oil supply pump 51, and a compression mechanism that compresses the lubricating oil discharged from the oil supply pump 51. And a discharge passage 53 leading to the discharge passage 40.

  FIG. 3 is a cross-sectional view schematically showing the configuration of the fuel pump.

  The refueling pump 51 is a so-called trochoid-type positive displacement pump, and is configured to be driven by the rotating shaft 30 via the pump driving shaft 33. Specifically, the refueling pump 51 includes a rotor housing 54, a trochoid-shaped inner rotor 55 and an outer rotor 56 housed in the rotor housing 54, and a port plate 57 on which the inner rotor 55 and the outer rotor 56 slide. have.

  Specifically, the rotor housing 54 is formed in a plate shape extending in the radial direction, and is fixed to the rear surface of the pump bearing member 31. At the center of the rear surface of the rotor housing 54, a rotor concave fitting portion 54b having a predetermined depth is provided. As shown in FIGS. 2 and 3, the rotor recessed portion 54 b is formed in a bottomed cylindrical shape with an open rear surface, and is formed in a radial direction with respect to the rotation axis X of the pump drive shaft 33 (the rotation shaft 30). Is eccentric by a predetermined amount. An insertion hole 54a that penetrates the rotor housing 54 in the axial direction is formed on the inner bottom surface of the rotor concave fitting portion 54b, and the pump drive shaft 33 is inserted therethrough. The rear end of the pump drive shaft 33 projects rearward from the inner bottom surface of the rotor recessed portion 54b.

  As shown in FIGS. 2 and 3, the inner rotor 55 is formed in a flat donut shape, and is housed in the rotor recessed portion 54b. A locking hole 55b is formed in the center of the inner rotor 55, and the pump drive shaft 33 is fitted into the locking hole 55b. By this fitting, the inner rotor 55 is arranged coaxially with the rotating shaft 30 and rotates in synchronization with the rotating shaft 30. The outer peripheral surface of the inner rotor 55 is provided with seven external teeth 55a having a trochoidal cross section.

  As shown in FIGS. 2 and 3, the outer rotor 56 is formed in a flat donut shape, and has an outer peripheral surface that is in sliding contact with the inner peripheral surface of the rotor recessed portion 54b. The inner peripheral surface of the outer rotor 56 is provided with eight internal teeth 56a having a trochoidal cross section and arranged so as to mesh with the external teeth 55a of the inner rotor 55. The outer rotor 56 rotates around the rotation axis eccentric to the rotation axis X of the inner rotor 55 by being rotated by the inner rotor 55.

  The port plate 57 is formed in a thin plate shape extending in the radial direction, and is attached to the rear surface of the rotor housing 54 so as to cover the open end of the recessed portion 54b.

  A pump chamber P is defined between the outer teeth 55a of the inner rotor 55 and the inner teeth 56a of the outer rotor 56. The pump chamber P is closed at both axial ends by the rotor recessed portion 54b and the port plate 57, and lubricating oil is sucked and discharged through a suction port 57a and a discharge port 57b formed in the port plate 57. It is configured as follows.

  The suction port 57a extends through the port plate 57 in the axial direction. When the inner rotor 55 and the outer rotor 56 rotate while meshing with each other (see an arrow in FIG. 3), the volume of the pump chamber P increases. It is open to. The discharge port 57b is recessed in the front surface of the port plate 57, and one end thereof opens to a range where the volume of the pump chamber P decreases when the inner rotor 55 and the outer rotor 56 rotate while meshing with each other. are doing. On the other hand, the other end of the discharge port 57b opens into the upstream oil supply hole 33a so that the pump chamber P communicates with the upstream oil supply hole 33a.

  Therefore, in the oil supply pump 51, the inner rotor 55 and the outer rotor 56 rotate while meshing with each other, so that the lubricating oil is sucked into the pump chamber P from the suction port 57a when the volume of the pump chamber P increases. At the same time, when the volume of the pump chamber P decreases, the fuel is discharged from the discharge port 57b to the outside of the pump chamber P (specifically, to the upstream oil supply hole 33a).

  The rotation speeds of the inner rotor 55 and the outer rotor 56 in the oil supply pump 51, and thus the supply amount of the lubricating oil per unit time, are proportional to the rotation speed of the rotating shaft 30 (hereinafter, referred to as "shaft rotation speed"). Will do.

  A pump cover 58 is attached to a rear surface of the port plate 57. The pump cover 58 is formed in a bottomed cylindrical shape with an open front side, and is arranged to cover the suction port 57a. An opening on the rear end side of the suction port 57a faces the inner bottom surface of the pump cover 58.

  An oil supply pipe 59 formed in a curved tubular shape is connected to the outer bottom surface of the pump cover 58. The refueling pipe 59 is bent so as to go substantially downward after going rearward. One of the open ends of the oil supply pipe 59 connected to the pump cover 58 opens into the storage chamber 58a, and the other open end is spaced apart from the inner bottom of the casing 11 by a predetermined distance in the vertical direction. It is arranged in an empty state and is immersed in the oil sump S1. The oil supply pipe 59 forms a suction passage 59a for guiding the lubricating oil to the storage chamber 58a.

  The suction passage 52 in this embodiment includes a suction passage 59a, a storage chamber 58a, and a suction port 57a. Lubricating oil forming an oil sump S1 in the casing 11 passes through the suction passage 52. Then, it is sucked into the pump chamber P of the refueling pump 51. The storage chamber 58a is interposed between the suction passage 59a and the suction port 57a, and is partitioned by the inner wall of the pump cover 58. A second oil reservoir S2 is formed in the storage chamber 58a.

  The discharge passage 53 in this embodiment includes a discharge port 57b, an upstream oil supply hole 33a, and an oil supply hole 30a. Lubricating oil discharged from the pump chamber P of the oil supply pump 51 passes through the discharge passage 53. The compressed air is supplied to the compression mechanism 40. Further, the lubricating oil flowing through the discharge passage 53 is also supplied to the pump bearing member 31, the scroll housing 41, the scroll bearing member 42b, and the like through a through hole 30b provided in the middle of the oil supply hole 30a.

  When the pressure of the lubricating oil discharged from the oil supply pump 51 (hereinafter, referred to as “discharge pressure”) is equal to or higher than a predetermined pressure, the lubricating mechanism 50 according to this embodiment transfers the lubricating oil from the discharge passage 53 to the suction passage 52. It is configured to be relieved (released) inside.

  Hereinafter, the configuration relating to the relief of the lubricating oil will be described in detail.

  As shown in FIG. 2, the oil supply mechanism 50 includes a relief port 57c that connects the discharge passage 53 to the suction passage 52, and a relief valve 62 that opens and closes the relief port 57c according to the discharge pressure of the lubricating oil. The relief valve 62 is disposed in the storage chamber 58a.

  The relief port 57c is provided at the inner bottom of the discharge port 57b (see FIG. 2), and penetrates the port plate 57 in the axial direction. Specifically, as shown in FIG. 2, one of the open ends of the relief port 57c is open in the discharge port 57b, and the other is open in the storage chamber 58a. More specifically, the latter open end is disposed inside the storage chamber 58a so as to face the inner wall of the storage chamber 58a (specifically, the inner bottom surface of the pump cover 58).

  The relief valve 62 is formed of a thin plate-shaped metal, and is fastened to the rear surface of the port plate 57 together with a retainer 63 configured as a relief valve holder. The relief valve 62 is formed so as to open and close the relief port 57c by bending and deforming according to the discharge pressure of the lubricating oil. Specifically, when the discharge pressure of the lubricating oil is equal to or higher than a predetermined pressure, the relief valve 62 is configured to be opened by the lubricating oil. The lubricating oil that has opened the relief valve 62 passes through the relief port 57c and is relieved into the storage chamber 58a. The relieved lubricating oil forms a second oil reservoir S2 in the storage chamber 58a.

  The retainer 63 is configured to limit the amount of bending of the relief valve 62, and prevents the relief valve 62 from being damaged.

  Therefore, when the compressor 10 starts operating, the rotary shaft 30 connected to the motor 20 drives the oil supply pump 51 via the pump drive shaft 33. When the refueling pump 51 is driven, the refueling mechanism 50 causes the lubricating oil sucked up from the oil sump S1 to be sucked into the refueling pump 51 through the suction passage 52 as shown by a black arrow in FIG. Is supplied to the compression mechanism 40 through the discharge passage 53.

  The discharge amount of the lubricating oil increases with an increase in the rotational speed of the shaft. As the discharge amount of the lubricating oil increases, the discharge pressure of the lubricating oil increases due to the passage resistance of the discharge passage 53 and the like. Will rise accordingly.

  As described above, when the discharge pressure of the lubricating oil is equal to or higher than the predetermined pressure, the lubricating mechanism 50 is configured to relieve the lubricating oil to the outside of the discharge passage 53. By performing lubrication oil relief, excessive supply of lubrication oil is prevented. Specifically, as shown by the white arrow in FIG. 2, the lubrication mechanism 50 supplies the lubricating oil from the discharge passage 53 (specifically, the discharge port 57 b) to the suction passage 52 (specifically, the storage chamber 58 a). It is configured to be relieved into. Since the open end of the relief port 57c is disposed to face the inner wall of the storage chamber 58a, the high-pressure lubricating oil that has passed through the relief port 57c is discharged toward the inner wall of the storage chamber 58a.

  According to this configuration, the relieved lubricating oil scatters not into the casing 11 but into the suction passage 52. In this case, since the lubricating oil scattered in the suction passage 52 floats as a droplet in the suction passage 52, it is isolated from the flow of the refrigerant gas flowing through the casing 11. Further, by scattering into the suction passage 52, the agitation of the oil pool S1 by the relieved lubricating oil is suppressed. Therefore, the amount of oil floating as splashes in the casing 11 and the amount of oil flowing out of the casing 11 along with the flow of the refrigerant gas are reduced.

  Thus, according to the above configuration, it is possible to prevent poor lubrication of the compression mechanism 40.

  In particular, when the compressor 10 is applied to a refrigeration cycle, it is possible to prevent the efficiency of the refrigeration cycle from deteriorating by reducing the oil rise as described above.

  Further, by preventing poor lubrication of the compression mechanism 40, it is advantageous for increasing the rotation speed of the compression mechanism 40, and further for reducing the size of the compressor 10. Hitherto, as one of measures for realizing downsizing of the compressor 10, increasing the rotation speed of the compression mechanism 40 has been considered. Generally, a large amount of lubricating oil is relieved in a high rotation range, so that the problem of poor lubrication caused by the lubricating oil relief as described above may become more serious. Therefore, the above configuration is effective in realizing a high rotation speed of the compression mechanism 40 and a miniaturization of the compressor 10 in that the lubricating oil can prevent poor lubrication caused by the relief of the lubricating oil. is there.

  Further, the relieved lubricating oil scatters into the storage chamber 58a and forms a second oil reservoir S2 in the storage chamber 58a. As described above, since the relieved lubricating oil is stored in the storage chamber 58a, the amount of oil returning to the oil sump S1 via the suction passage 52 can be reduced. This is advantageous in that the agitation of the oil sump S1 by the relieved lubricating oil is suppressed, and thus poor lubrication of the compression mechanism 40 is prevented.

  Furthermore, according to the above configuration, the relieved lubricating oil is isolated from the gas flowing through the casing 11 because it is isolated in the storage chamber 58a. Therefore, the amount of oil flowing out of the casing 11 along with the flow of the gas refrigerant is reduced, which is advantageous in preventing poor lubrication of the compression mechanism 40.

  FIG. 3 shows the flow of gas refrigerant between the compressor 10 according to this embodiment, which is configured to relieve into the storage chamber 58a, and the conventional compressor, which is configured to relieve toward the oil sump S1. 4 is a graph comparing measurement results of a flow rate of lubricating oil flowing out of a casing 11 upon riding (hereinafter, referred to as “oil discharge amount”). The horizontal axis in FIG. 3 is the shaft rotation speed, and the vertical axis is the oil discharge amount. Further, a solid line indicates an oil discharge amount of the compressor 10 according to the embodiment, and a broken line indicates an oil discharge amount of the conventional compressor. As shown in FIG. 3, it can be seen that the compressor 10 according to this embodiment has a smaller oil discharge amount than the compressor according to the conventional configuration. This reflects the fact that, as described above, the amount of oil floating in the casing 11 as droplets and the amount of oil flowing out of the casing 11 along with the flow of the refrigerant gas are reduced.

  Providing the storage chamber 58 a in the middle of the suction passage 52 is effective in securing a space for mounting the relief valve 62 in the suction passage 52.

  Further, when a positive displacement pump is applied as the refueling pump 51, compared to the case where a centrifugal pump is applied, it is possible to suppress the amount of refueling in a high rotation range and to prevent excessive refueling. Therefore, by combining with the above-described configuration for preventing the lubrication failure of the compression mechanism 40, it is possible to prevent both the excessive lubrication and the lubrication failure, and to perform the lubrication to the compression mechanism 40 without excess or shortage. become.

  Also, it is generally considered that in the case of a horizontal type compressor, it is necessary to make the passage length of the suction passage longer than that of a vertical type compressor as described in Patent Document 1. Since the compressor 10 according to this embodiment is of a horizontal type, it is advantageous in that the storage chamber 58a is provided in the middle of the suction passage 52 as the passage length of the suction passage 52 is increased.

<Other embodiments>
The above embodiment may have the following configuration.

  The configuration of the compressor 10 is an example, and is not limited to this configuration. For example, in the above-described embodiment, the casing 11 is disposed so that the axial direction of the rotating shaft 30 is along the horizontal direction, but the present invention is not limited to this. The casing 11 may be arranged so that the axial direction of the rotating shaft 30 is along the vertical direction. That is, the compressor 10 is not limited to the horizontal type, and may be a vertical type.

  Further, in the above-described embodiment, the oil supply pump 51 is configured as a positive displacement pump, but is not limited thereto. The refueling pump 51 may be configured as, for example, a centrifugal pump.

DESCRIPTION OF SYMBOLS 10 Compressor 11 Casing 20 Motor 30 Rotary shaft 30a Oil supply hole 40 Compression mechanism 50 Oil supply mechanism 51 Oil supply pump 52 Suction passage 53 Discharge passage 57c Relief port 58a Storage chamber 62 Relief valve S1 Oil sump S2 Second oil sump

Claims (6)

A casing through which gas flows,
A compression mechanism housed in the casing and configured to compress the gas;
An oil supply mechanism having an oil supply pump, a suction passage for guiding lubricating oil forming an oil reservoir in the casing to the oil supply pump, and a discharge passage for guiding lubricating oil discharged from the oil supply pump to the compression mechanism. ,
A storage chamber communicating with the discharge passage via the oil supply pump is defined in the suction passage,
In the storage room,
A suction port communicating the storage chamber with the refueling pump;
A discharge port forming a part of the discharge passage and a relief port communicating with the storage chamber are open,
The lubrication mechanism is configured to relieve the lubricating oil at the discharge port into the storage chamber via the relief port when a discharge pressure of the lubricating oil discharged from the refueling pump is equal to or higher than a predetermined pressure. A compressor characterized by the above-mentioned. The compressor according to claim 1,
The said storage room forms the 2nd oil sump, The compressor characterized by the above-mentioned . The compressor according to claim 2,
The refueling mechanism,
Said relief port,
A relief valve that opens and closes the relief port according to the discharge pressure of the lubricating oil,
The compressor according to claim 1, wherein the relief valve is provided in the storage chamber. In the compressor according to any one of claims 1 to 3,
The said oil supply pump is a positive displacement pump, The compressor characterized by the above-mentioned. In the compressor according to any one of claims 1 to 4,
A motor housed in the casing,
A rotating shaft connected to the motor and driving the compression mechanism and the oil supply mechanism;
An oil supply hole extending in the axial direction of the rotary shaft is formed inside the rotary shaft,
The said oil supply hole comprises the said discharge passage, The compressor characterized by the above-mentioned. The compressor according to claim 5,
The compressor, wherein the casing is arranged such that an axial direction of the rotating shaft is along a horizontal direction.

Images