COMPRESSOR
A compressor includes a compression mechanism housed in a casing. The compression mechanism includes a suction volume adjustment mechanism capable of switching a suction completion position of a compression chamber in a suction process between a first position and a second position with a smaller suction volume than the first position. The suction volume adjustment mechanism includes a plunger switchable between a closed position in which the suction completion position is moved to the first position and an open position in which the suction completion position is moved to the second position. An oil passage is arranged to allow an oil reservoir formed inside the casing and a suction space of the compression chamber to communicate with each other. The plunger is disposed midway along the oil passage, and includes a switching portion closing the oil passage in the closed position, and opening the oil passage in the open position.
The present disclosure is directed to a compressor including a suction bypass mechanism configured to change a position at which a suction process is completed and a compression process is started (hereinafter referred to as “suction completion position”) to adjust a suction volume. The present disclosure relates to a technique of solving lubricant shortage in a compression mechanism.
BACKGROUND ARTIn conventional compressors, inverters are widely used to allow the compressors to be used in various operations ranging from an operation at a high rotational speed to an operation at a low rotational speed. Generally, during an operation at a high rotational speed, the flow rate of a refrigerant inside a compressor is increased. This increases the amount of refrigerating machine oil to be sucked together with the refrigerant to be supplied to a compression mechanism of the compressor, resulting in an increase in the amount of the refrigerating machine oil to be discharged together with the refrigerant compressed. Therefore, it has been desired to reduce the amount of refrigerating machine oil to be supplied to the interior of the compression mechanism.
It has been suggested to provide a capacity adjusting mechanism to a compression mechanism in order to achieve performance of inverter control not only when a compressor is operated at a high rotational speed (hereinafter referred to as “the operation at the high operation capacity”) but also when the compressor is operated at a low rotational speed (hereinafter referred to as “the operation at the low operation capacity” (See Patent Document 1). At the low operation capacity, the operation is generally performed at a low rotational speed, and its performance is lower at the low rotational speed than at the high rotational speed. In order to reduce performance degradation at the low rotational speed, it is preferable to allow the capacity adjusting mechanism to reduce the suction volume to increase the rotational speed.
For example, Patent Document 1 discloses a suction bypass mechanism which adjusts a suction volume by changing a suction completion position in a scroll compressor. The suction bypass mechanism of Patent Document 1 includes a plunger (valve) serving as an opening/closing mechanism allowing first and second compression chambers to switch between a communicating state and a shut-off state, the first compression chamber being provided between the inner peripheral surface of a fixed scroll and the outer peripheral surface of an orbiting scroll, and the second compression chamber being provided between the outer peripheral surface of the fixed scroll and the inner peripheral surface of the orbiting scroll. If this suction bypass mechanism allows the first and second compression chambers to communicate with each other, the suction completion position is changed from the position of the shut-off state to a position in which the suction volume is reduced. According to this configuration, in a situation where the operation capacity is substantially constant, a smaller suction volume allows the compression mechanism to be operated at a high rotational speed. This can achieve its performance.
CITATION LIST Patent Document[Patent Document 1] Japanese Unexamined Patent Publication No. 2007-154761
SUMMARY OF THE INVENTION Technical ProblemHowever, in a situation where the compressor is controlled at a low operation capacity, if the compressor is tried to be rotated at a higher speed than a situation where the capacity is not controlled, its performance can be less reduced than the situation where the capacity is not controlled. However, oil to be supplied to the compression chamber is insufficient due to the low operation capacity, and an oil film is not sufficiently formed inside the compression mechanism, resulting in insufficient performance.
That is to say, if oil loss at the high rotation capacity is reduced, oil supply necessary for forming the oil film inside the compression mechanism at the low operation capacity is also insufficient. Thus, in the compressor, it is actually difficult to reduce performance degradation at the low operation capacity and oil loss at the high operation capacity.
In view of the foregoing background, it is therefore an object of the present disclosure to provide a technique of improving performance of a compressor at a low operation capacity while reducing oil loss at a high operation capacity.
Solution to the ProblemA first aspect of the present disclosure is directed to a compressor including: a compression mechanism (20); and a casing (10) housing the compression mechanism (20), the compression mechanism (20) including a suction volume adjustment mechanism (30) capable of switching a suction completion position of a compression chamber (25a, 25b) in a suction process between a first position and a second position in which the suction volume is smaller than in the first position, the suction volume adjustment mechanism (30) including a plunger (33) switchable between a closed position in which the suction completion position is moved to the first position and an open position in which the suction completion position is moved to the second position.
This compressor further includes an oil passage (51) to allow an oil reservoir (18, 50) formed inside the casing (10) and a suction space (25s) of the compression chamber (25a, 25b) to communicate with each other, and the plunger (33) is disposed midway of the oil passage (51), and includes a switching portion (65) closing the oil passage (51) in the closed position to allow the oil reservoir (18, 50) not to communicate with the suction space (25s) of the compression chamber (25a, 25b), and opening the oil passage (51) in the open position to allow the oil reservoir (50) to communicate with the suction space (25s) of the compression chamber (25a, 25b).
According to the first aspect, if the suction completion position is in the first position, the plunger (33) is in the closed position. At that time, the oil passage (51) is blocked, and thus, no oil is supplied from the oil reservoir (18, 50) to the suction space (25s) of the compression chamber (25a, 25b). In contrast, if the suction completion position is in the second position, in which the suction volume is reduced, the plunger (33) is in the open position. At that time, the oil passage (51) is opened, and thus, oil is supplied from the oil reservoir (18, 50) to the suction space (25s) of the compression chamber (25a, 25b) by a negative pressure in the suction space (25s).
A second aspect of the present disclosure is an embodiment of the first aspect of the present disclosure. In the second aspect, the compression mechanism (20) is a compression mechanism (20) including a fixed scroll (21), and an orbiting scroll (22) meshing with the fixed scroll (21) and compressing a working fluid.
According to the second aspect, if in the scroll compressor, the suction completion position is in the first position and the plunger (33) is in the closed position, the oil passage (51) is blocked. Thus, no oil is supplied from the oil reservoir (18, 50) to the suction space (25s) of the compression chamber (25a, 25b). If the suction completion position is in the second position and the plunger (33) is in the open position in which the suction volume is reduced, the oil passage (51) is opened. Thus, oil is supplied from the oil reservoir (18, 50) to the suction space (25s) of the compression chamber (25a, 25b) by the negative pressure.
A third aspect of the present disclosure is an embodiment of the second aspect of the present disclosure. In the third aspect, the oil passage (51) has one end communicating with the oil reservoir (50) formed in a crank chamber (23e) that is a space inside the housing (23) of the compression mechanism (20), and the other end communicating with the suction space (25s) of the compression mechanism (20).
According to the third aspect, if the suction completion position is in the second position and the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) is opened. Thus, oil is supplied from the oil reservoir (18, 50) formed in the space (the crank chamber (23e)) inside the housing of the compression mechanism (20) to the suction space (25s) of the compression chamber (25a, 25b) by the negative pressure.
A fourth aspect of the present disclosure is an embodiment of the second aspect of the present disclosure. In the fourth aspect, the oil passage (51) includes an orbiting-scroll-side oil passage (55) and a fixed-scroll-side oil passage (52) communicating with the orbiting-scroll-side oil passage (55), the orbiting-scroll-side oil passage (55) has one end communicating with the fixed-scroll-side oil passage (52), and the other end opposite to one end and communicating with the oil reservoir (50), and the fixed-scroll-side oil passage (52) has one end communicating with the orbiting-scroll-side oil passage (55), and the other end opposite to one end and communicating with the suction space (25s) of the compression mechanism (20).
According to the fourth aspect, if the suction completion position is in the second position and the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) comprised of the orbiting-scroll-side oil passage (55) and the fixed-scroll-side oil passage (52) is opened. Thus, oil is supplied from the oil reservoir (18, 50) to the suction space (25s) of the compression chamber (25a, 25b) by the negative pressure.
A fifth aspect of the present disclosure is an embodiment of the second aspect of the present disclosure. In the fifth aspect, the oil passage (51) has an oil supply pipe (56) having one end communicating with the oil reservoir (18) formed inside the casing (10), and the other end communicating with the suction space (25s) of the compression mechanism (20).
According to the fifth aspect, if the suction completion position is in the second position and the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) is opened. Thus, oil is supplied from the oil reservoir (18, 50) formed in the casing (10) to the suction space (25s) of the compression chamber (25a, 25b) by the negative pressure.
A sixth aspect of the present disclosure is an embodiment of the second aspect of the present disclosure. In the sixth aspect, the oil passage (51) has an oil supply pipe (57) having one end communicating with an oil supply pump (43a) provided to a drive shaft of the compression mechanism (20), and the other end communicating with the suction space (25s) of the compression mechanism (20).
According to the sixth aspect, if the suction completion position is in the second position and the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) is opened. Thus, oil is supplied from the oil supply pump (43a) to the suction space (25s) of the compression chamber (25a, 25b).
A seventh aspect of the present disclosure is an embodiment of any one of the third to sixth aspects of the present disclosure. In the seventh aspect, the oil passage (51) has a fixed scroll inner passage (53) passing through an interior of the fixed scroll (21) to communicate with the plunger (33) and the suction space (25s) of the compression mechanism (20).
According to the seventh aspect, if the suction completion position is in the second position and the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) is opened. Thus, oil is supplied to the suction space (25s) of the compression chamber (25a, 25b) through the fixed scroll inner passage (53) in the interior of the fixed scroll (21).
An eighth aspect of the present disclosure is an embodiment of any one of the third to sixth aspects of the present disclosure. In the eighth aspect, the oil passage (51) has a fixed scroll outer passage (58) passing through a space formed outside the fixed scroll (21) and inside the casing (10) to communicate with the plunger (33) and the suction space (25s) of the compression mechanism (20).
According to the eighth aspect, if the suction completion position is in the second position and the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) is opened. Thus, oil is supplied from the oil reservoir (18, 50) formed in the casing (10) to the suction space (25s) of the compression chamber (25a, 25b) through the space formed outside the fixed scroll (21) and inside the casing (10).
A ninth aspect of the present disclosure is an embodiment of any one of the third to sixth aspects of the present disclosure. In the ninth aspect, the suction volume adjustment mechanism (30) has a discharge passage (60) discharging the working fluid from the plunger (33) in the second position into a space formed outside the fixed scroll (21) and inside the casing (10), and the oil passage (51) has an oil mix passage (53a) having one end communicating with the plunger (33), and the other end communicating with the discharge passage (60).
According to the ninth aspect, if the suction completion position is in the second position and the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) including the oil mix passage (53a) communicating with the discharge passage (60) is opened. Thus, oil is supplied from the oil reservoir (18, 50) formed in the casing (10) to the suction space (25s) of the compression chamber (25a, 25b) through the space formed outside the fixed scroll (21) and inside the casing (10).
A tenth aspect of the present disclosure is an embodiment of any one of the one to ninth aspects of the present disclosure. In the tenth aspect, the plunger (33) is a cylindrical valve body, and has an outer surface provided with a circumferential groove (33d) that is disposed on the oil passage (51) in the second position and is deviated from the oil passage (51) in the first position.
An eleventh aspect of the present disclosure is an embodiment of the tenth aspect of the present disclosure. In the eleventh aspect, the plunger (33) includes a sealing member (33e) at both sides of the circumferential groove (33d) formed in the outer surface of the plunger (33).
Advantages of the InventionAccording to the first aspect of the present disclosure, if the suction completion position is in the first position and no capacity control is performed, the plunger (33) is in the closed position to block the oil passage (51). This operation is the operation performed a high operation capacity, and the flow rate of the refrigerant inside the compressor is increased. Thus, oil is sufficiently sucked into the compression chambers (25a, 25b) and excessive oil is not supplied from the oil passage (51) to the compression chambers (25a, 25b). This reduces oil loss while maintaining its performance.
In contrast, if the suction completion position is in the second position and the capacity is controlled such that the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) is opened. This operation is the operation performed a low operation capacity, and the flow rate of the refrigerant inside the compressor is decreased. Therefore, although oil mixed in the refrigerant is insufficiently sucked into the compression chambers (25a, 25b), oil is supplied from the oil passage (51) to the compression chambers (25a, 25b) as well. According to the first aspect of the present disclosure, at that time, the oil film can be sufficiently formed in the interior of the compression mechanism, compared to the case where the capacity of the compressor is not controlled. This can improve performance of the compressor.
According to the second aspect of the present disclosure, in the scroll compressor, if the suction completion position is in the first position and no capacity control is performed, the plunger (33) is in the closed position to block the oil passage (51). This operation is the operation performed a high operation capacity, and the flow rate of the refrigerant inside the compressor is increased. Thus, oil is sufficiently sucked into the compression chambers (25a, 25b) and excessive oil is not supplied from the oil passage (51) to the compression chambers (25a, 25b). This reduces oil loss while maintaining its performance.
In contrast, if the suction completion position is in the second position and the capacity is controlled such that the suction volume is reduced, the plunger (33) is in the open position and the oil passage (51) is opened. This operation is the operation performed a low operation capacity, and the flow rate of the refrigerant inside the compressor is decreased. Therefore, although oil mixed in the refrigerant is insufficiently sucked into the compression chambers (25a, 25b), oil is supplied from the oil passage (51) to the compression chambers (25a, 25b) as well. According to the second aspect of the present disclosure, at that time, the oil film can be sufficiently formed in the interior of the compression mechanism, compared to the case where the capacity of the compressor is not controlled. This can improve performance of the compressor.
According to the third aspect of the present disclosure, oil can be supplied to the compression chambers (25a, 25b) during adjustment of the suction volume using the oil passage (51) having one end communicating with the oil reservoir (18, 50) formed in the space inside the housing (23) of the compression mechanism (20) (the crank chamber (23e)), and the other end communicating with the suction space (25s) of the compression mechanism (20). Therefore, this can improve performance of the scroll compressor with a simple configuration.
According to the fourth aspect of the present disclosure, oil can be supplied to the compression chambers (25a, 25b) during adjustment of the suction volume, using the oil passage (51) comprised of the orbiting-scroll-side oil passage (55) and the fixed-scroll-side oil passage (52), and having one end communicating with the oil reservoir (18, 50) and the other end communicating with the suction space (25s) of the compression mechanism (20). Therefore, this can reduce performance degradation of the scroll compressor and oil loss with a simple configuration.
According to the fifth aspect of the present disclosure, oil can be supplied to the compression chambers (25a, 25b) during adjustment of the suction volume using the oil passage (51) having one end communicating with the oil reservoir (18, 50) formed in the casing (10) of the compressor, and the other end communicating with the suction space (25s) of the compression mechanism (20). Therefore, this can improve performance of the scroll compressor with a simple configuration.
According to the sixth aspect of the present disclosure, oil can be supplied to the compression chambers (25a, 25b) during adjustment of the suction volume using the oil passage (51) having one end communicating with the oil supply pump (43a), and the other end communicating with the suction space (25s) of the compression mechanism (20). Therefore, this can improve performance of the scroll compressor with a simple configuration.
According to the seventh aspect of the present disclosure, oil can be supplied to the compression chambers (25a, 25b) during adjustment of the suction volume using the oil passage (51) having the fixed scroll inner passage (53) passing through the inside of the fixed scroll (21) to communicate with the plunger (33) and the suction space (25s) of the compression mechanism (20). Therefore, this can improve performance of the scroll compressor with a simple configuration.
According to the eighth aspect of the present disclosure, oil can be supplied to the compression chambers (25a, 25b) during adjustment of the suction volume using the oil passage (51) having the fixed scroll outer passage (58) passing through the space formed outside the fixed scroll (21) and inside the casing (10) to communicate with the plunger (33) and the suction space (25s) of the compression mechanism (20). Therefore, this can improve performance of the scroll compressor with a simple configuration.
According to the ninth aspect of the present disclosure, oil can be supplied to the compression chambers (25a, 25b) during adjustment of the suction volume using the oil passage (51) having the oil mix passage (53a) communicating with the discharge passage (60) discharging the working fluid from the plunger (33) into the space formed outside the fixed scroll (21) and inside the casing (10). Therefore, this can improve performance of the scroll compressor with a simple configuration.
According to the tenth aspect of the present disclosure, a suction volume adjustment mechanism (30) can be provided with a simple configuration having the plunger (33) that is a cylindrical valve body. According to the eleventh aspect of the present disclosure, the plunger (33) is provided with the sealing member (33e), thereby making it possible to reduce oil leakage.
Embodiments of the present disclosure will now be described in detail with reference to the drawings.
First EmbodimentA first embodiment of the present disclosure is now described.
A scroll compressor according to this embodiment is provided to, e.g., a refrigerant circuit of an air conditioner performing a vapor compression refrigeration cycle, and compresses a low-pressure refrigerant that has been sucked from an evaporator to discharge it into a condenser.
As illustrated in
This casing (10) houses a compression mechanism (20) compressing a refrigerant, and an electric motor (45) driving the compression mechanism (20). The electric motor (45) is disposed below the compression mechanism (20), and is coupled to the compression mechanism (20) through a drive shaft (40) that is a rotational shaft. The electric motor (45) is implemented as a brushless DC motor controlled by an inverter to adjust a rotational speed to be variable.
A discharge pipe (15) passes through and is attached to the upper end plate (12) that is a top of the casing (10). This discharge pipe (15) has its terminal end (the lower end in the figure) connected to the compression mechanism (20). A suction pipe (14) passes through and is attached to the body (11) of the casing (10). This suction pipe (14) has its terminal end (the right end in the figure) open toward a space between the compression mechanism (20) and the electric motor (45) in the casing (10).
The drive shaft (40) is disposed on the vertical center line of the casing (10). The drive shaft (40) is a crank shaft including a main shaft portion (41) and an eccentric portion (42). The eccentric portion (42) has a smaller diameter than the main shaft portion (41), and is formed on the upper surface of the main shaft portion (41). The eccentric portion (42) is eccentric from the axial center of the main shaft portion (41) by a predetermined dimension, and constitutes an eccentric pin.
A lower bearing holder (48) is fixed to a portion adjacent to the lower end of the body (11) of the casing (10). This lower bearing holder (48) rotatably supports the lower end of the main shaft portion (41) of the drive shaft (40) through a sliding bearing (48a).
The interior of the drive shaft (40) is provided with an oil supply passage (44) extending vertically. The lower end of the main shaft portion (41) is provided with an oil supply pump (43). This oil supply pump (43) sucks refrigerating machine oil from the bottom of the casing (10). The refrigerating machine oil passes through the oil supply passage (44) of the drive shaft (40) to be supplied to the sliding portion of the compression mechanism (20) and the bearing of the drive shaft (40).
The electric motor(45) is comprised of a stator (46) and a rotor (47). The stator (46) is fixed to the body (11) of the casing (10). The rotor (47) is coupled to the main shaft portion (41) of the drive shaft (40) to drive the drive shaft (40) in rotation.
The compression mechanism (20) includes a fixed scroll (21), an orbiting scroll (22), and a housing (23) fixing and supporting the fixed scroll (21). The fixed scroll (21) and the orbiting scroll (22) respectively include spiral laps (21b, 22b) meshing with each other on end plates (21a, 22a), which will be described later. The compression mechanism (20) is configured such that the orbiting scroll (22) rotates eccentrically relative to the fixed scroll (21).
The housing (23) is comprised of a body (23a) and a bearing holder (23b). The body (23a) is formed to be vertically continuous with the bearing holder (23b), and the body (23a) is fitted into and coupled to the body (11) of the casing (10). The bearing holder (23b) has a smaller diameter than the body (23a), and protrudes downward from the body (23a). The bearing holder (23b) rotatably supports the main shaft portion (41) of the drive shaft (40) through a sliding bearing (23c).
The fixed scroll (21) is comprised of a fixed end plate (21a), a fixed lap (21b), and an edge portion (21c). The fixed end plate (21a) is formed to have a substantially disk shape. The fixed lap (21b) stands near the middle portion of the lower surface of the fixed end plate (21a), and is integrally formed with the fixed end plate (21a). The fixed lap (21b) is formed to have a spiral wall shape with a constant height. The edge portion (21c) is a wall extending downward from the outer peripheral portion of the fixed end plate (21a), and has a lower surface overlapping with the upper surface of the body (23a) of the housing (23) to be fixed to the housing (23).
The orbiting scroll (22) is comprised of an orbiting end plate (22a), an orbiting lap (22b), and a boss (22c). The orbiting end plate (22a) is formed to have a substantially disk shape. The orbiting lap (22b) stands on the upper surface of the orbiting end plate (22a), and is integrally formed with the orbiting end plate (22a). The orbiting lap (22b) is formed to have a spiral wall shape with a constant height, and to mesh with the fixed lap (21b) of the fixed scroll (21). The boss (22c) extends downwardly from the lower surface of the orbiting end plate (22a), and integrally formed with the orbiting end plate (22a).
The eccentric portion (42) of the drive shaft (40) is inserted into the boss (22c) through a sliding bearing (22d). Therefore, if the drive shaft (40) rotates, the orbiting scroll (22) revolves around the axial center of the main shaft portion (41). The revolution radius of the orbiting scroll (22) is the same as the eccentricity of the eccentric portion (42), i.e., a distance from the axial center of the main shaft portion (41) to the axial center of the eccentric portion (42).
The orbiting end plate (22a) is disposed in a first recess (23d) provided to the upper end of the housing (23). The boss (22c) is disposed in a second recess (a crank chamber) (23e) provided to the body (23a) of the housing (23). Although not shown, the Oldham coupling is disposed between the orbiting end plate (22a) and the housing (23) to prevent the orbiting scroll (22) from rotating on its axis. The first recess (23d) is formed large enough to allow the orbiting end plate (22a) to rotate eccentrically, and the second recess (23e) is formed large enough to allow the boss (22c) to rotate eccentrically (the size relation therebetween is not considered on the figures).
The compression mechanism (20) includes a plurality of compression chambers (25a, 25b) in a space between the fixed end plate (21a) and the orbiting end plate (22a). The compression chambers (25a, 25b) are defined by allowing the fixed lap (21b) to mesh with the orbiting lap (22b). The plurality of the compression chambers (25a, 25b) include a plurality of first compression chambers (25a) and a plurality of second compression chambers (25b). The first compression chamber (25a) is defined by a space between the inner peripheral surface of the fixed lap (21b) and the outer peripheral surface of the orbiting lap (22b). The second compression chamber (25b) is defined by a space between the outer peripheral surface of the fixed lap (21b) and the inner peripheral surface of the orbiting lap (22b). In this embodiment, the number of turns or windings of the fixed lap (21b) is greater than that of the orbiting lap (22b), and thus, the maximum capacity of the first compression chamber (25a) is larger than that of the second compression chamber (25b).
As shown in
The upper end of the fixed end plate (21a) is provided with a depression (21g), and a discharge cover (27) is attached to the upper surface of the fixed end plate (21a) to cover a depression (21g). A space where the depression (21g) is covered with the discharge cover (27) is a discharge chamber (28) communicating with the discharge pipe (15). A middle lower portion of the fixed end plate (21a) is provided with a discharge port (26) communicating with the discharge chamber (28). The discharge port (26), along with the revolution of the orbiting scroll (22), intermittently communicates with the first compression chamber (25a) and the second compression chamber (25b). In this embodiment, in the interior of the casing (10), both upper and lower spaces (16) and (17) of the housing (23) are low-pressure spaces filled with a low-pressure refrigerant.
In this embodiment, as shown in
The opening/closing mechanism (31), as shown in
As shown in
The communication passage (32) is a stepped hole (32) formed in the fixed end plate (21a). As shown in
A compression coil spring (a biasing member) (35) and the plunger (33) (see
As shown in
Although the specific operation of the suction volume adjustment mechanism (30) (opening/closing mechanism (31)) will be described later, if the suction volume adjustment mechanism (30) is operated with the plunger (33) in the closed position, the first and second compression chambers (25a) and (25b) do not communicate with each other. Thus, a normal operation in which the refrigerant is compressed with a set suction volume is performed. In contrast, if the suction volume adjustment mechanism (30) is operated with the plunger (33) in the open position, the first and second compression chambers (25a) and (25b) communicate with each other. Thus, an adjustment operation is performed in which the refrigerant is compressed with a less suction volume than a set value. In this embodiment, the rotational speed of the electric motor (45) is faster during this adjustment operation than during the normal operation.
In the casing (10), an oil reservoir (50) is formed in the bottom of the second recess (the crank chamber) (23e) to reserve oil that has lubricated the bearing of the drive shaft (41) and other components. The compression mechanism (20) in this embodiment is provided with an oil passage (51) communicating with the oil reservoir (50) and a suction space (25s) of the compression chambers (25a, 25b). The oil passage (51) has one end communicating with the oil reservoir (50) formed in the crank chamber (23e) in the housing (23) of the compression mechanism (20), and the other end communicating with the suction space (25s) of the compression mechanism (20). The oil passage (51), as shown in
The plunger (33) is disposed midway of the transverse passage (53) of the oil passage (51). The plunger (33) includes a switching portion (55). This switching valve (55) closes the oil passage (51) in the closed position to allow the oil reservoir (50) not to communicate with the suction space (25s) of the compression chambers (25a, 25b), and opens the oil passage (51) in the open position to allow the oil reservoir (50) to communicate with the suction space (25s) of the compression chambers (25a, 25b). This switching portion (55) is configured as the circumferential groove (33d) formed in the sealing portion (33c). That is to say, in the open position in
Next, it will be described how the scroll compressor (1) stated above is operated.
First, if the electric motor (45) is driven, the drive shaft (40) rotates and the orbiting scroll (22) revolves relative to the fixed scroll (21). At that time, the Oldham coupling (not shown) prevents the fixed scroll (21) from rotating on its axis.
Along with the revolution of the orbiting scroll (22), volumes of the compression chambers (25a, 25b) increase and decrease repeatedly and periodically. In the compression chambers (25a, 25b), the refrigerant in the refrigerant circuit is sucked from the suction pipe (14) through a suction passage (not shown) and the suction port (29) into the compression chambers (25a, 25b) when the volume of a portion, communicating with the suction port (29), of the compression chambers (25a, 25b) is increased, and the refrigerant in the refrigerant circuit is compressed and discharged from the discharge port (26) to the discharge chamber (28) when the volume of a portion in which a suction side is closed decreases. The refrigerant in the discharge chamber (28) is supplied from the discharge pipe (15) to the condenser in the refrigerant circuit.
Operation of Compression Mechanism During Normal OperationThe refrigerant suction and compression operations of the compression mechanism (20) when the suction volume adjustment mechanism (30) is not operated (during the normal operation) will be described with reference to
First, in the first operation state shown in
From this state, the orbiting scroll (22) revolves in the clockwise direction in the figure to be in the second operation state in
From this state, if the orbiting scroll (22) revolves to be in the third operation state in
In the fifth operation state shown in
Thereafter, the operations in
During the normal operation, in the suction volume adjustment mechanism (30), the plunger (33) is in the closed position and the oil passage (51) is blocked. As a result, the oil reservoir (50) does not communicate with the suction space (25s) of the compression chambers (25a, 25b). Therefore, during the normal operation at the high operation capacity, the discharge of the oil is small, and along with this, no oil is supplied from the oil reservoir (50) to the compression chambers (25a, 25b), and oil is not excessively supplied to the compression chambers.
Operation of Compression Mechanism During Adjustment OperationLikewise, the refrigerant suction and compression operations of the compression mechanism (20) when the suction volume adjustment mechanism (30) is operated (during the adjustment operation) will be described with reference to
First, in the first operation state shown in
In the second operation state in
This position is also seen in the third operation state shown in
In the fifth operation state shown in
As can be seen, the communication passage (32) of the opening/closing mechanism (31) is opened, and thus, the volume of the first compression chamber (25a) and the volume of the second compression chamber (25b) is smaller than during the normal operation. As a result, a compression ratio is smaller than during the normal operation, and if its suction pressure is the same as during the normal operation, the discharge pressure is decreased.
During this adjustment operation, the rotational speed of the electric motor (45) is faster than during the normal operation, and thus, substantially the same performance of the scroll compressor (1) as in the normal operation can be achieved.
During the adjustment operation, in the suction volume adjustment mechanism (30), the plunger (33) is in the open position and the oil passage (51) is opened to allow the oil reservoir (50) to communicate with the suction space (25s) of the compression chambers (25a, 25b). Therefore, during the adjustment operation at the low operation capacity, the performance is adjusted to provide the same capacity, and thus, the rotational speed is faster than in the case where no adjustment is made. This increases the supply amount of the oil to the compression chambers (25a, 25b), and in addition, allows oil from the oil reservoir (18, 50) to the compression chambers (25a, 25b). As a result, oil is sufficiently supplied to the compression chambers (25a, 25b).
Advantages of First EmbodimentAccording to this embodiment, if only the adjustment operation at the low operation capacity is performed, oil is not sufficiently supplied to the compression chambers (25a, 25b), and the oil film having a thickness necessary for the compression mechanism (20) is not formed, resulting in performance degradation. However, if the oil passage (51) is opened and the oil reservoir (50) communicates with the suction space (25s) of the compression chambers (25a, 25b), oil is sufficiently supplied to the compression chambers (25a, 25b). Thus, this can improve performance during the adjustment operation.
Variation of First EmbodimentAs shown in
According to this variation, if only the adjustment operation at the low operation capacity is performed, oil is not sufficiently supplied to the compression chambers (25a, 25b), and the oil film having a thickness necessary for the compression mechanism is less likely to be formed, resulting in performance degradation. However, in this variation, if the oil passage (51) is in the state in
Next, a second embodiment will be described.
In the second embodiment, as shown in
According to this second embodiment, if only the adjustment operation at the low operation capacity is performed, oil is not sufficiently supplied to the compression chambers (25a, 25b), and the oil film having a thickness necessary for the compression mechanism is less likely to be formed, resulting in performance degradation. However, in the second embodiment, if the oil passage (51) is in the state in
Next, a third embodiment will be described.
In the third embodiment, as shown in
The other configuration of this embodiment is the same as, or similar to, that of the second embodiment.
According to this third embodiment, if only the adjustment operation at the low operation capacity is performed, oil is not sufficiently supplied to the compression chambers (25a, 25b), and the oil film having a thickness necessary for the compression mechanism is less likely to be formed, resulting in performance degradation. However, in the third embodiment, if the oil passage (51) is in the state in
Next, a fourth embodiment will be described.
In the fourth embodiment, as shown in
The other configuration of this embodiment is the same as, or similar to, that of the third embodiment.
According to this fourth embodiment, if only the adjustment operation at the low operation capacity is performed, oil is not sufficiently supplied to the compression chambers (25a, 25b), and the oil film having a thickness necessary for the compression mechanism is less likely to be formed, resulting in performance degradation. However, in the fourth embodiment, if the oil passage (51) is in the state in
Next, a fifth embodiment will be described.
In the fifth embodiment, as shown in
According to this configuration, as shown in
According to this fifth embodiment, if only the adjustment operation at the low operation capacity is performed, oil is not sufficiently supplied to the compression chambers (25a, 25b), and the oil film having a thickness necessary for the compression mechanism is less likely to be formed, resulting in performance degradation. However, in the fifth embodiment, if the oil passage (51) is in the state in
A sixth embodiment of the present disclosure is an example and has the same configuration as the fifth embodiment, except the configuration for the oil passage (51). Specifically, as shown in
According to this configuration, as shown in
According to this sixth embodiment, if only the adjustment operation at the low operation capacity is performed, oil is not sufficiently supplied to the compression chambers (25a, 25b), and the oil film having a thickness necessary for the compression mechanism is less likely to be formed, resulting in performance degradation. However, in the sixth embodiment, if the oil passage (51) is in the state in
The above-described embodiment may be modified as follows.
For example, the above embodiments are the examples where the present disclosure is applied to the asymmetrical spiral structure. The present disclosure may also be applied to a scroll compressor having a symmetrical spiral structure. In this case, the suction volume adjustment mechanism (30) having the same or similar configuration as or to those in the above embodiments may be provided to each symmetrical position relative to the center of the spiral. Such a configuration allows the compression mechanism (20) having the symmetrical spiral structure to adjust the suction completion positions of the first and second compression chambers (25a) and (25b) relative to the center of the spiral, while controlling the flow of the oil. As a result, the same or similar advantages in the above embodiments can also be obtained.
In the above embodiments, the present disclosure is applied to the scroll compressor. However, the present disclosure is not limited to the scroll compressor. For example, the present disclosure may also be applied to a rolling piston compressor or an oscillating piston compressor.
Further, in the above embodiments, as shown in
Note that the foregoing description of the embodiments is a merely preferred example in nature, and is not intended to limit the scope, application, or uses of the present disclosure.
INDUSTRIAL APPLICABILITYAs can be seen from the foregoing description, the present disclosure is useful for, in a compressor including a suction bypass mechanism configured to change a suction completion position to adjust a suction volume, a technique of solving lubricant shortage in a compression mechanism.
DESCRIPTION OF REFERENCE CHARACTERS
- 1 Scroll Compressor
- 10 Casing
- 18 Oil Reservoir
- 21 Fixed Scroll
- 22 Orbiting Scroll
- 23 Housing
- 23e Crank Chamber
- 25a Compression Chamber
- 25b Compression Chamber
- 25s Suction Space
- 30 Suction Volume Adjustment Mechanism
- 33 Plunger
- 33d Circumferential Groove
- 33e Sealing Member
- 43a Oil Supply Pump
- 50 Oil Reservoir
- 51 Oil Passage
- 52 Fixed-scroll-side Oil Passage (Fixed Scroll Inner Passage)
- 53 Fixed-scroll-side Oil Passage (Fixed Scroll Inner Passage)
- 53a Oil Mix Passage
- 55 Orbiting-scroll-side Oil Passage
- 56 Oil Supply Pipe
- 57 Oil Supply Pipe
- 58 Fixed Scroll Outer Passage
- 60 Gas Discharge Passage
- 65 Switching Portion
Claims
1. A compressor comprising:
- a compression mechanism; and
- a casing housing the compression mechanism,
- the compression mechanism including a suction volume adjustment mechanism capable of switching a suction completion position of a compression chamber in a suction process between a first position and a second position in which a suction volume is smaller than in the first position,
- the suction volume adjustment mechanism including a plunger switchable between a closed position in which the suction completion position is moved to the first position and an open position in which the suction completion position is moved to the second position,
- the compressor further including an oil passage arranged to allow an oil reservoir formed inside the casing and a suction space of the compression chamber to communicate with each other, and
- the plunger being disposed midway along the oil passage, and including a switching portion closing the oil passage in the closed position to allow the oil reservoir not to communicate with the suction space of the compression chamber, and opening the oil passage in the open position to allow the oil reservoir to communicate with the suction space of the compression chamber.
2. The compressor of claim 1, wherein
- the compression mechanism includes a fixed scroll, and an orbiting scroll meshing with the fixed scroll to compress a working fluid.
3. The compressor of claim 2, wherein
- the oil passage has one end communicating with the oil reservoir and an other end communicating with the suction space of the compression mechanism, and
- the oil reservoir is formed in a crank chamber that is a space inside the housing of the compression mechanism.
4. The compressor of claim 2, wherein
- the oil passage includes an orbiting-scroll-side oil passage and a fixed-scroll-side oil passage communicating with the orbiting-scroll-side oil passage,
- the orbiting-scroll-side oil passage has one end communicating with the fixed-scroll-side oil passage, and an other end opposite to the one end thereof communicating with the oil reservoir, and
- the fixed-scroll-side oil passage has one end communicating with the orbiting-scroll-side oil passage, and an other end opposite to the one end thereof communicating with the suction space of the compression mechanism.
5. The compressor of claim 2, wherein
- the oil passage has an oil supply pipe having one end communicating with the oil reservoir, and an other end communicating with the suction space of the compression mechanism.
6. The compressor of claim 2, wherein
- the oil passage has an oil supply pipe having one end communicating with an oil supply pump provided to a drive shaft of the compression mechanism, and an other end communicating with the suction space of the compression mechanism.
7. The compressor of claim 3, wherein
- the oil passage has a fixed scroll inner passage passing through an interior of the fixed scroll to communicate with the plunger and the suction space of the compression mechanism.
8. The compressor of claim 3, wherein
- the oil passage has a fixed scroll outer passage passing through a space formed outside the fixed scroll and inside the casing to communicate with the plunger and the suction space of the compression mechanism.
9. The compressor of claim 3, wherein
- the suction volume adjustment mechanism has a discharge passage arranged to discharge the working fluid from the plunger in the second position into a space formed outside the fixed scroll and inside the casing, and
- the oil passage has an oil mix passage having one end communicating with the plunger, and an other end communicating with the discharge passage.
10. The compressor of claim 1, wherein
- the plunger is a cylindrical valve body, and has an outer surface provided with a circumferential groove that is disposed on the oil passage in the second position and is deviated from the oil passage in the first position.
11. The compressor of claim 10, wherein
- the plunger includes a sealing member at both sides of the circumferential groove formed in the outer surface of the plunger.
12. The compressor of claim 4, wherein
- the oil passage has a fixed scroll inner passage passing through an interior of the fixed scroll to communicate with the plunger and the suction space of the compression mechanism.
13. The compressor of claim 4, wherein
- the oil passage has a fixed scroll outer passage passing through a space formed outside the fixed scroll and inside the casing to communicate with the plunger and the suction space of the compression mechanism.
14. The compressor of claim 4, wherein
- the suction volume adjustment mechanism has a discharge passage arranged to discharge the working fluid from the plunger in the second position into a space formed outside the fixed scroll and inside the casing, and
- the oil passage has an oil mix passage having one end communicating with the plunger, and an other end communicating with the discharge passage.
15. The compressor of claim 5, wherein
- the oil passage has a fixed scroll inner passage passing through an interior of the fixed scroll to communicate with the plunger and the suction space of the compression mechanism.
16. The compressor of claim 5, wherein
- the oil passage has a fixed scroll outer passage passing through a space formed outside the fixed scroll and inside the casing to communicate with the plunger and the suction space of the compression mechanism.
17. The compressor of claim 5, wherein
- the suction volume adjustment mechanism has a discharge passage arranged to discharge the working fluid from the plunger in the second position into a space formed outside the fixed scroll and inside the casing, and
- the oil passage has an oil mix passage having one end communicating with the plunger, and an other end communicating with the discharge passage.
18. The compressor of claim 6, wherein
- the oil passage has a fixed scroll inner passage passing through an interior of the fixed scroll to communicate with the plunger and the suction space of the compression mechanism.
19. The compressor of claim 6, wherein
- the oil passage has a fixed scroll outer passage passing through a space formed outside the fixed scroll and inside the casing to communicate with the plunger and the suction space of the compression mechanism.
20. The compressor of claim 6, wherein
- the suction volume adjustment mechanism has a discharge passage arranged to discharge the working fluid from the plunger in the second position into a space formed outside the fixed scroll and inside the casing, and
- the oil passage has an oil mix passage having one end communicating with the plunger, and an other end communicating with the discharge passage.
Type: Application
Filed: Oct 24, 2016
Publication Date: Oct 18, 2018
Inventor: Masahiro YAMADA (Osaka-shi, Osaka)
Application Number: 15/765,235