CN115875232A - Compressor and heat exchange system - Google Patents
Compressor and heat exchange system Download PDFInfo
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- CN115875232A CN115875232A CN202210798896.7A CN202210798896A CN115875232A CN 115875232 A CN115875232 A CN 115875232A CN 202210798896 A CN202210798896 A CN 202210798896A CN 115875232 A CN115875232 A CN 115875232A
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Abstract
The invention provides a compressor and a heat exchange system capable of ensuring enough jet force for opening a spitting valve and reducing pressure loss. The plurality of compression mechanisms of the compressor respectively include: a cylinder (60) having a refrigerant suction path; a roller (62) that eccentrically rotates by rotation of the rotating shaft; a blade (63) which is in contact with the outer peripheral surface of the roller (62) and separates the interior of the cylinder (60) into two spaces; a bearing having a bearing discharge port (80); a discharge valve which is provided so as to block the bearing discharge port (80) and is lifted by the refrigerant compressed by the rotation of the roller (62) to discharge the refrigerant; a partition plate (68) having a partition plate discharge port (81); and a discharge valve which is arranged to block the partition plate discharge port (81), and is lifted by the refrigerant compressed by the rotation of the roller (62), and discharges the refrigerant. The positions of the bearing discharge port (80) and the partition plate discharge port (81) in the direction perpendicular to the axial direction are offset by a predetermined distance or more.
Description
Technical Field
The present invention relates to a compressor having a plurality of compression mechanisms and a heat exchange system.
Background
In a heat exchange system such as an air conditioner, a rotary compressor is used as a compressor for compressing a refrigerant and circulating the refrigerant in the system. The rotary compressor includes a hollow cylindrical body (cylinder tube) and a rotating body (roller) that rotates in the cylinder tube as a compression mechanism, and compresses refrigerant gas sucked into the cylinder tube by the rotation of the roller in the cylinder tube.
The rotary compressor has two compression mechanisms, one compression chamber is formed by sealing the upper side of one cylinder tube by a main bearing and the lower side by a partition plate, the other compression chamber is formed by sealing the upper side of the other cylinder tube by the partition plate and the lower side by a lower bearing. In this case, the refrigerant gas compressed in each compression chamber is discharged through each discharge path provided in each of the main bearing and the lower bearing.
In order to increase the discharge capacity of the compressor without increasing the size of the compressor too much, the cross-sectional area of the hole of the discharge path can be increased to enlarge the discharge path. However, simply increasing the cross-sectional area of one hole causes the discharge valve provided in the discharge path to deform due to an increase in stress when the differential pressure between the inside and the outside of the compression chamber is pressed into the compression chamber, which reduces reliability.
Therefore, a compressor has been proposed in which a discharge path is provided also in a partition plate that partitions upper and lower compression chambers, and one compression chamber includes two discharge paths (see, for example, patent document 1). In this compressor, an angle formed by a straight line connecting the center and a position where the roller contacts the cylinder wall surface and a direction in which the vane contacting the roller and dividing the compression chamber into two parts extends is defined as a crank angle about a rotation axis for rotating the roller, and the discharge path provided in the partition plate is provided at about 350 ° in crank angle substantially the same as the discharge path provided in the main bearing and the lower bearing.
Documents of the prior art
Patent literature
Patent document 1: japanese patent No. 6022247
Disclosure of Invention
Problems to be solved by the invention
The discharge valve provided in each discharge path is opened by the discharge force of the refrigerant gas flowing into the discharge path. As the crank angle approaches 350 °, the holes of the discharge path connected to the compression chamber are closed by the roller, and the flow rate gradually decreases, but in a configuration in which one discharge path is provided for one compression chamber, a sufficient jet force can be obtained even when the crank angle exceeds 270 °.
However, in the conventional technique described above, since the two discharge paths are equally distributed during one rotation of the roller and the flow rate per one discharge path is reduced, if the crank angle exceeds 270 °, a jet flow force sufficient to open the discharge valve cannot be obtained, and discharge from a small gap occurs, which causes a problem of large pressure loss.
Means for solving the problems
In view of the above-described problems, the present invention provides a compressor having a plurality of compression mechanisms, the compressor being characterized in that,
each compression mechanism includes:
a hollow cylindrical body having a suction path for sucking a refrigerant;
a rotating body which eccentrically rotates by rotation of a rotating shaft disposed at the center in the cylindrical body;
a separation means that is in contact with the outer peripheral surface of the rotating body and separates the cylindrical body into two spaces;
a first covering member that has a first discharge path and covers one axial end of the rotating shaft of the cylindrical body;
a first discharge valve which is provided so as to close the first discharge path, and which is lifted by the refrigerant compressed by the rotation of the rotating body to discharge the refrigerant;
a second covering member that has a second discharge path and covers the other end of the cylindrical body in the axial direction of the rotating shaft; and
a second discharge valve which is provided so as to close the second discharge path and is lifted by the refrigerant compressed by the rotation of the rotary body to discharge the refrigerant,
the positions of the first discharge path and the second discharge path in the direction perpendicular to the axial direction are offset by a predetermined distance or more.
Effects of the invention
According to the present invention, it is possible to provide a compressor and a heat exchange system capable of reducing pressure loss by securing a sufficient injection force for opening a discharge valve.
Drawings
Fig. 1 is a diagram showing a configuration example of an air conditioner as an example of a heat exchange system.
Fig. 2 is a diagram illustrating a refrigerant circuit of the air conditioner.
Fig. 3 is a diagram showing main components of a compressor provided in an outdoor unit.
Fig. 4 is a diagram showing a configuration example of the motor.
Fig. 5 is a diagram showing a configuration example of the compression mechanism.
Fig. 6 is a diagram showing a first configuration example of the compressor.
Fig. 7 is a diagram showing valve operation in a case where the position of the orifice provided in the discharge path of the partition plate is changed.
Fig. 8 is a diagram showing a second configuration example of the compressor.
Fig. 9 is a diagram showing a third configuration example of the compressor.
Fig. 10 is a diagram showing a fourth configuration example of the compressor.
Fig. 11 is a diagram showing a fifth configuration example of the compressor.
In the figure:
10-air conditioning apparatus, 11-indoor unit, 12-outdoor unit, 13-remote controller, 20-indoor heat exchanger, 21-indoor fan, 22-driving motor for indoor fan, 30-compressor, 31-accumulator, 32-four-way valve, 33-expansion valve, 34-outdoor heat exchanger, 35-outdoor fan, 36-driving motor for outdoor fan, 37-control device, 40-casing, 41-upper cover, 42-lower cover, 43-suction pipe, 44-seal, 45-discharge pipe, 46-electric motor, 47-compression mechanism, 50-stator, 51-rotor, 52-wire, 53-rotation shaft, 54-eccentric cam, 55-blade, 56-oil supply, 60-upper cylinder, 61-main bearing, 62-roller, 63-blade, 64-spring, 65-discharge valve, 66-holder, 67-upper discharge cover, 68-partition plate, 70-lower cylinder, 71-lower bearing, 72-roller, 73-blade, 74-spring, 75-discharge valve, 76-holder, 67-upper discharge cover, 68-partition plate, 70-lower cylinder, 71-lower bearing, 72-discharge valve holder, 81-outlet port, 85 a, and first discharge port.
Detailed Description
The heat exchange system of the present embodiment is a system that exchanges heat between a fluid and a refrigerant, and circulates the refrigerant in a closed system, heats or cools the fluid sucked in by exchanging heat with the circulating refrigerant, and discharges the fluid. The fluid may be a gas such as air, or a liquid such as water or a solution. The heat exchange system includes a compressor, a heat exchanger, and an expansion valve in order to heat and cool a refrigerant in the system. Examples of such a heat exchange system including a compressor, a heat exchanger, and an expansion valve include an air conditioner, a cooler (cooling water circulation device), and a refrigerator.
Fig. 1 is a diagram showing a configuration example of an air conditioner. Here, the heat exchange system will be described as an air conditioner. The air conditioner 10 includes an indoor unit 11 installed in a space (indoor) to be air-conditioned, an outdoor unit 12 installed outdoors, and a remote controller 13 operated by a user, and performs air conditioning by circulating a refrigerant between the indoor unit 11 and the outdoor unit 12 and exchanging heat with indoor air. Therefore, the indoor unit 11 and the outdoor unit 12 are connected by two refrigerant pipes 14 and 15 for circulating the refrigerant.
The indoor units 11 and the outdoor units 12 may be respectively configured by two or more, or two or more indoor units 11 may be connected to one outdoor unit 12. Hydrofluorocarbon (HFC) can be used as the refrigerant, and R-410A, R-32 and the like can be mentioned as the type of HFC.
The indoor unit 11 performs wireless communication using infrared rays or the like with the remote controller 13, and receives various signals such as an operation command, a stop command, a set temperature change command, and an operation mode change command. The indoor unit 11 is connected to the outdoor unit 12 via a communication line, and performs indoor air conditioning in cooperation with the outdoor unit 12.
The indoor unit 11 is activated upon receiving an operation command from the remote controller 13, and instructs the outdoor unit 12 to activate. After the outdoor unit 12 is started, the rotation speed of the compressor, the opening degree of the expansion valve, and the like are adjusted, and the circulation amount of the refrigerant and the like are controlled so that the indoor temperature becomes the set temperature.
The refrigerant circuit of the air-conditioning apparatus 10 will be briefly described with reference to fig. 2. The arrows shown in fig. 2 indicate the flow of the refrigerant during the cooling operation, and the operation during the cooling operation will be mainly described. In the heating operation, the refrigerant flows in the opposite direction.
The indoor unit 11 includes an indoor heat exchanger 20, an indoor fan 21, and an indoor fan drive motor 22. The indoor fan 21 is driven by an indoor fan drive motor 22, and sucks indoor air into the indoor heat exchanger 20. The indoor heat exchanger 20 includes a heat transfer pipe through which the refrigerant flows, and the introduced air contacts the surface of the heat transfer pipe to exchange heat. The air heat-exchanged by the indoor heat exchanger 20 is discharged into the room.
In addition, the indoor unit 11 may include various sensors for measuring an indoor temperature and the like, an expansion valve, and the like.
The outdoor unit 12 includes a compressor 30, an accumulator 31, a four-way valve 32, an expansion valve 33, an outdoor heat exchanger 34, an outdoor fan 35, and an outdoor fan drive motor 36. The compressor 30 is driven by a compressor drive motor, compresses a low-pressure gas refrigerant, and discharges the compressed gas refrigerant as a high-pressure gas refrigerant. The accumulator 31 is a container for storing the returned liquid at the time of transition, and adjusts the refrigerant to an appropriate dryness. The dryness is a ratio of the vapor in the wet vapor representing a mixed state of the vapor and the fine droplets.
The four-way valve 32 is a valve for switching the flow path of the refrigerant according to the operation state (operation mode) of the air conditioner 10. The operation modes include a cooling mode, a heating mode, and an air blowing mode. The expansion valve 33 is a valve that decompresses and expands the high-pressure refrigerant. The outdoor fan 35 is driven by an outdoor fan drive motor 36, and draws in outdoor air to send the air to the outdoor heat exchanger 34. The outdoor heat exchanger 34 has a heat transfer tube through which the refrigerant flows inside, as in the indoor heat exchanger 20, and the sent air contacts the surface of the heat transfer tube to exchange heat. The air heat-exchanged by the outdoor heat exchanger 34 is discharged to the outside.
The outdoor unit 12 includes a control device 37. The controller 37 is connected to and controls the compressor 30, the four-way valve 32, the expansion valve 33, the indoor fan drive motor 22, and the outdoor fan drive motor 36. Specifically, the control of the rotation speed of the compressor 30, the opening degree of the expansion valve 33, the rotation speeds of the indoor fan drive motor 22 and the outdoor fan drive motor 36, and the like is performed. Various sensors are also installed in the outdoor unit 12 to control these. The control device 37 performs control of these based on information detected by various sensors.
In the cooling operation, the indoor heat exchanger 20 is used as an evaporator, and the outdoor heat exchanger 34 is used as a condenser. Therefore, the controller 37 circulates the refrigerant sealed in the system as indicated by the arrow in the order of the compressor 30, the outdoor heat exchanger 34, the expansion valve 33, the indoor heat exchanger 20, the four-way valve 32, the accumulator 31, and the compressor 30.
The compressor 30 compresses a low-temperature low-pressure refrigerant (refrigerant gas) in a gas state, and discharges the compressed refrigerant into a high-temperature high-pressure refrigerant gas. The outdoor heat exchanger 34 exchanges heat with outdoor air to cool and condense the refrigerant gas. The expansion valve 33 reduces the pressure of the refrigerant and partially vaporizes the refrigerant. Therefore, the refrigerant is supplied to the indoor unit 11 in a gas-liquid mixed state. The expansion valve 33 is adjusted in opening degree by the control device 37 so as to have an appropriate amount of liquid.
The indoor heat exchanger 20 exchanges heat with indoor air, and the condensed liquid refrigerant is entirely vaporized and returned to the outdoor unit 12 as a refrigerant gas. The refrigerant gas returned from the indoor heat exchanger 20 is sent to the accumulator 31 through the four-way valve 32, and returned to the compressor 30.
The controller 37 is attached to the outdoor unit 12, but is not limited thereto, and may be attached to the indoor unit 11, other central control boards, and the like.
The heat exchange system can employ a rotary compressor as the compressor 30. A rotary compressor compresses a refrigerant by a combination of a hollow cylindrical body (cylinder tube) having a suction path for sucking the refrigerant and a rotating body (roller) eccentrically rotated by rotation of a rotating shaft disposed at the center in the cylinder tube.
The main components of the compressor 30 provided in the outdoor unit 12 will be described with reference to fig. 3. The compressor 30 includes a hollow cylindrical casing 40, an upper cover 41 covering an upper portion of the casing 40, and a lower cover 42 covering a lower portion of the casing 40, and a closed space is formed by them. The casing 40 is provided with a suction pipe 43, and the suction pipe 43 is connected to the accumulator 31 via a seal 44, and sucks the refrigerant gas from the accumulator 31 during the cooling operation. The upper cover 41 is provided with a discharge pipe 45, and the discharge pipe 45 can supply the refrigerant gas compressed by the compressor 30 to the outdoor heat exchanger 34 during the cooling operation.
A motor 46 and a compression mechanism 47 constituting the compressor 30 are accommodated in a space sealed by the housing 40, the upper cover 41, and the lower cover 42, and a refrigerant gas is sucked and compressed by the compression mechanism 47 driven by the motor 46. In this example, the compression mechanism 47 is provided in two stages, i.e., an upper stage and a lower stage, and the compressed refrigerant gas is discharged into a space between the motor 46 and the upper stage compression mechanism 47 and a space between the lower stage compression mechanism 47 and the lower cap 42, is sent to a space between the motor 46 and the upper cap 41 through the compression mechanism 47 and a gap between the motor 46 and the casing 40, and is discharged from the discharge pipe 45 provided in the upper cap 41.
The structure of the motor 46 will be described in detail with reference to fig. 4. The motor 46 includes a stator (stator) 50 and a rotor (rotor) 51. The stator 50 has a coil to which an electric wire 52 for supplying current is connected. The rotor 51 is a permanent magnet or the like, and rotates by passing a current through the coil.
A hole having a predetermined diameter is formed in the center of the rotor 51, and a rotary shaft 53 can be inserted and mounted therein. An eccentric cam 54 is provided on the outer periphery of the rotating shaft 53 so as to be able to eccentrically rotate the roller. Here, the compression mechanism 47 has two stages, and the rollers are provided in the two stages, so the eccentric cam 54 has two stages.
The rotary shaft 53 has a hollow space extending in the axial direction from the lower end, and a paddle 55 and an oil feeder 56 for drawing up the refrigerating machine oil filled between the lower cover 42 and the lower compression mechanism 47 and supplying the oil to a sliding portion such as a space between the cylinder tube and the roller are provided in the hollow space. The refrigerating machine oil has high lubricity and is supplied for reducing wear of sliding parts. Since the refrigerating machine oil is discharged from the compression mechanism 47 together with the refrigerant gas, it needs to be returned to the stored lower cover 42, and has a property of being fused with the refrigerant to some extent (refrigerant compatibility). The refrigerating machine oil discharged to the compression mechanism 47 together with the refrigerant gas is in a mist form, falls onto the inclined compression mechanism 47, flows on the inclined surface, falls through a discharge hole communicating toward the lower cover 42 provided at the edge of the compression mechanism 47, and returns to the lower cover 42.
The structure of the compression mechanism 47 will be described in detail with reference to fig. 5. Fig. 5 is a diagram showing an example in which the compression mechanism 47 is provided in two layers. The upper compression mechanism is composed of an upper cylinder 60, a main bearing 61, a roller 62, a vane 63, a spring 64, a discharge valve 65, a discharge valve holder (holder) 66, an upper discharge cap 67, and a partition plate 68.
The lower compression mechanism is composed of a lower cylinder 70, a lower bearing 71, a roller 72, a vane 73, a spring 74, a discharge valve 75, a holder 76, a lower discharge cap 77, and a partition plate 68. The partition plate 68 is a member that partitions the upper stage and the lower stage, and is used in common for both the compression mechanisms. Since the lower stage compression mechanism has the same structure and operates in the same manner as the upper stage compression mechanism, only the upper stage compression mechanism will be described here.
The upper cylinder 60 is a hollow cylindrical body, and has a groove and a hole for accommodating the blade 63 and the spring 64 functioning as the separation means. Inside the upper cylinder 60, a hollow cylindrical roller 62 is accommodated. One end of the blade 63 abuts on the outer peripheral surface of the roller 62, and the other end thereof is engaged with the spring 64, and the state of being pressed against the roller 62 is maintained by the spring 64. The spring 64 is provided such that one end thereof is engaged with the other end of the blade 63 and the other end thereof abuts against the inner surface of the housing 40.
An eccentric cam 54 of a rotation shaft 53 is inserted into the roller 62. The roller 62 is eccentrically rotated in the upper cylinder 60 by the rotation of the rotary shaft 53. The vane 63 separates the inside of the upper cylinder 60 into two spaces while maintaining a state of being in contact with the outer peripheral surface of the roller 62. The upper cylinder 60 is provided with a suction path continuous with one of the two spaces separated by the vane 63, and the refrigerant gas sucked from the suction pipe 43 is supplied.
The main bearing 61 is rotatably supported on the rotating shaft 53 together with the lower bearing 71. The main bearing 61 covers one axial direction of the rotary shaft 53 of the upper cylinder 60, and has a discharge path for discharging the compressed refrigerant gas. The discharge valve 65 is provided in the discharge path, is lifted by the jet force of the refrigerant gas, and discharges the refrigerant gas to the space above the main bearing 61 through the gap. The upper discharge cap 67 is disposed on the main bearing 61 and functions as a muffler for muffling the sound emitted from the discharged refrigerant gas. The discharge valve 65 lifted by the jet force of the refrigerant gas is held in shape by the retainer 66 without being deformed. The discharge valve 65 can be returned to its original position by the retainer 66 to close the discharge path when the jet force of the refrigerant gas is reduced.
The partition plate 68 covers the other axial side of the rotary shaft 53 of the upper cylinder 60 and has a discharge path for discharging the compressed refrigerant gas. A discharge valve and a retainer are also provided in the discharge path, and the discharge valve is lifted by the jet force of the refrigerant gas, and discharges the refrigerant gas to a space provided in the partition plate 68 through the gap. The space provided in the partition plate 68 is connected to a discharge path provided in the rim of the upper cylinder 60 together with the bolt hole, and the refrigerant gas is discharged to the space between the upper cylinder 60 and the upper discharge cap 67 through the discharge path.
Now, a case where two discharge paths are provided for one compression chamber, that is, two discharge paths are provided for both of main bearing 61 and partition plate 68, and lower bearing 71 and partition plate 68, is described, and the positions where two discharge paths are provided will be described below.
Fig. 6 is a diagram showing a first configuration example of the compressor. Fig. 6 (base:Sub>A) isbase:Sub>A view showing the structure of the compressor 30 described with reference to fig. 3 to 5, and fig. 6 (b) isbase:Sub>A cross-sectional view taken along the cutting linebase:Sub>A-base:Sub>A in fig. 6 (base:Sub>A). Fig. 6 (C) is a cross-sectional view taken along the cutting line B-B in fig. 6 (B), and fig. 6 (d) is an enlarged view of a portion indicated by the area C in fig. 6 (C).
As shown in fig. 6 (b), in the upper cylinder 60, the roller 62 eccentrically rotates, and one end of the vane 63 abuts on the outer peripheral surface of the roller 62. The upper cylinder 60 has bolt holes or the like in its edge portion, and has a groove continuous with the inner space and accommodating the vane 63. The blade 63 slides in the groove while maintaining a state in which one end thereof is in contact with the outer peripheral surface of the roller 62.
In fig. 6 (b), the direction in which the blades 63 extend is set to 0 ° in crank angle in the horizontal direction perpendicular to the axial direction of the rotating shaft 53, and the discharge path (first bearing discharge port) 80 provided in the main bearing 61 is present at a position along the inner surface of the upper cylinder 60 at about 350 ° in crank angle. The refrigerant gas suction path is formed so as to be continuous with a space (suction-side space) formed on the opposite side of the first bearing discharge port 80 with the vane 63 interposed therebetween.
In fig. 6 (b), the position in the vertical direction perpendicular to the axial direction of the rotating shaft 53 of the discharge path (first partition plate discharge port) 81 provided in the partition plate 68 is deviated from the position in the vertical direction of the first bearing discharge port 80 by a predetermined distance or more and is present at a position along the inner surface of the upper cylinder 60 and in the vicinity of a crank angle of 270 °.
As shown in fig. 6 (d), the first partition plate discharge port 81 is continuous with a flow channel 82 provided in a space in the partition plate 68. The partition plate 68 is provided with discharge valves 83 and 84 and retainers 85 and 86, similarly to the main bearing 61. Therefore, the discharge valves 83 and 84 are opened by the jet force of the refrigerant gas, and the refrigerant gas is discharged into the flow path 82. The refrigerant gas discharged to the flow path 82 is discharged to a space above the main bearing 61 through the discharge path, further moves to a space between the motor 46 and the upper cap 41 through a gap between the motor 46 and the housing 40, and is discharged from the discharge pipe 45.
The flow rate of the discharged gas of the rotary compressor decreases as the crank angle approaches 360 °. For example, when the roller 62 is located at a position of 180 ° in crank angle, the blade 63 separates the space on the low pressure side where the suction path exists and the space on the high pressure side where the first bearing discharge port 80 and the first partition plate discharge port 81 exist. The roller 62 is eccentrically rotated, and the outer peripheral surface of the roller 62 is moved from the crank angle of 180 ° to 360 ° while being in contact with the inner surface of the upper cylinder 60, and the movement reduces the space on the high pressure side, thereby reducing the flow rate of the discharged gas.
In a section where the high-pressure side space is large and the flow rate of the discharged gas is large, such as 180 ° to 270 ° in crank angle, even if the horizontal position of the first partition plate discharge port 81 and the horizontal position of the first bearing discharge port 80 are substantially the same, the pressure loss can be reduced by discharging the gas from both the discharge ports.
However, when the crank angle exceeds 270 °, the space on the high-pressure side becomes small, and the flow rate of the discharge gas becomes small, the flow rate per one discharge port becomes too small due to the distribution to the two discharge ports, the force pushing up the discharge valve 65 becomes insufficient, the discharge is performed from a small flow path, and the pressure loss increases. If the pressure loss increases, a desired flow rate cannot be obtained, and the performance is affected.
As shown in fig. 6 (b), the first partition plate discharge port 81 and the first bearing discharge port 80 are not arranged coaxially, but are displaced so that in a section where the flow rate is large, discharge is performed from both the first bearing discharge port 80 and the first partition plate discharge port 81, and in a section where the crank angle is close to 350 ° and the flow rate is reduced, discharge is performed from only one discharge port, i.e., the first bearing discharge port 80. This prevents the flow rate from becoming too small and the force for pushing up the discharge valve from becoming insufficient, and thus can suppress an increase in pressure loss.
Specifically, the first bearing discharge port 80 is provided at about 350 ° in crank angle, and the first partition plate discharge port 81 is provided at about 270 ° in crank angle. When the roller 62 is present at a position where the crank angle is 200 °, for example, the first partition plate discharge port 81 is not closed by the roller 62, and therefore, the discharge can be performed from two discharge ports, i.e., the first bearing discharge port 80 and the first partition plate discharge port 81. When the roller 62 approaches the 270 ° position, the first separator discharge port 81 is gradually blocked by the roller 62, and when the roller reaches the vicinity of 270 °, the first separator discharge port 81 is blocked. Therefore, the fluid is discharged only from the first bearing discharge port 80.
Thereafter, the first partition plate discharge port 81 is gradually opened by the movement of the roller 62, but the refrigerant gas is not pushed up and is not discharged because the refrigerant gas is at a low pressure side continuously with the space on the low pressure side.
The valve operation when the position of the orifice provided in the discharge path of the partition plate 68 is changed will be described with reference to fig. 7. In fig. 7, the left side view is a view showing an example of a case where the first bearing discharge port 80 and the first partition plate discharge port 81 are positioned on the same axis at about 350 ° in crank angle. The center diagram is a diagram showing an example of a case where the first bearing discharge port 80 is located at around 350 ° in crank angle, but the first partition plate discharge port 81 is located at around 270 ° in crank angle, and the position thereof is shifted. The right side of the drawing shows an example in which the first bearing discharge port 80 is positioned at about 350 ° in crank angle, but the first partition plate discharge port 81 is positioned at about 240 ° in crank angle, and the position is shifted.
The valve operation shows the crank angle (deg), the lift (mm), and the flow passage area (mm) as the operation of the discharge valve during the cooling operation 2 ) The relationship (2) of (c). In each figure, the lift amount and the flow path area of the discharge valve 65 on the main bearing 61 side, and the lift amount and the flow path area of the discharge valve 83 on the partition plate 68 side are shown in accordance with the crank angle. In each figure, a parameter obtained by summing up the two flow path areas is also shown.
Referring to the left drawing, the discharge valve is opened from around 200 ° in crank angle, and the lift amount and flow path area are the largest near 240 ° in crank angle, and are substantially 0 near 310 ° in crank angle, and thereafter, discharge is not performed. This is because, since both the first bearing discharge port 80 and the first partition plate discharge port 81 are provided at about 350 ° in crank angle and distributed to the two discharge ports, the flow rate per discharge port becomes excessively small after 310 ° in crank angle, and the force for pushing up the discharge valves 65 and 83 becomes insufficient.
Referring to the center diagram, the discharge valve is opened from around 200 ° in crank angle, and the lift amount and the flow path area are maximized around 240 ° in crank angle. However, when the crank angle is 270 °, the first partition plate discharge port 81 of the partition plate 68 is blocked by the roller 62, and the lift amount and the flow path area become 0.
After the crank angle is 270 °, since only the first bearing discharge port 80 of the main bearing 61 is open, the discharge valve 65 is opened and the refrigerant is discharged until the crank angle is around 330 ° without the flow rate becoming too small as in the left drawing.
Referring to the right drawing, the discharge valve is opened from around 200 ° in crank angle, and the lift amount and flow path area are maximized around 240 ° in crank angle. In the example shown in the figure, when the crank angle is in the vicinity of 240 °, the first partition plate discharge port 81 of the partition plate 68 is blocked by the roller 62, and the lift amount and the flow path area become 0.
After the crank angle is 240 °, only the first bearing discharge port 80 of the main bearing 61 is opened, and therefore, the discharge valve 65 is opened to a crank angle of about 330 ° without the flow rate becoming excessively small, as in the example shown in the center drawing, and the refrigerant is discharged. In the example shown in the right-hand drawing, the first partition plate discharge port 81 is blocked earlier than in the example shown in the center drawing, and as a result, the period during which the lift amount and the flow path area of the discharge valve 65 on the main bearing 61 side become maximum becomes longer.
According to these results, the first bearing discharge port 80 can be provided at a position close to the crank angle of 350 ° as in the conventional case, and the first partition plate discharge port 81 can be provided at a position deviated from the first bearing discharge port 80 by a predetermined distance or more and at a crank angle of 240 ° or 270 °. The positions of these discharge ports are examples, and therefore the discharge ports are not limited to these positions, and for example, the first bearing discharge port 80 may be provided at a crank angle of 330 ° to 355 °, and the first partition plate discharge port 81 may be provided at a crank angle of 220 ° to 300 °.
The high-temperature refrigerant gas flowing into the first partition plate discharge port 81 passes through the flow path 82 provided in the space in the partition plate 68 and is finally discharged into the sealed casing constituted by the casing 40, the upper cover 41, and the lower cover 42. When the flow path 82 is provided in the partition plate 68, the thickness of the partition plate 68 that partitions the space in the upper cylinder 60, the space in the lower cylinder 70, and the flow path 82 is reduced only in the portion of the flow path 82.
When the flow path 82 is provided, for example, below the space on the suction side of the refrigerant gas at a crank angle of 0 ° to 180 ° in the upper cylinder 60, the temperature of the refrigerant gas in the space on the suction side is low, and therefore, the heat of the high-temperature refrigerant gas flowing through the flow path 82 transfers heat to the low-temperature refrigerant gas in the upper cylinder 60 via the partition plate 68, and the temperature of the refrigerant gas discharged into the sealed gas decreases. When the temperature of the refrigerant gas decreases, there is a possibility that the refrigerant gas condenses, and if the refrigerant gas condenses and remains, the refrigerant gas is not discharged.
Therefore, the flow path 82 can be formed such that the space on the suction side where the low-temperature refrigerant gas exists and the flow path 82 provided in the space in the partition plate 68 do not overlap in the axial direction of the rotary shaft 53.
Fig. 8 is a diagram showing a second configuration example of the compressor. The main structure of the compressor 30 is the same as that shown in fig. 6 (a). Fig. 8 isbase:Sub>A sectional view taken at the same position as the cutting linebase:Sub>A-base:Sub>A in fig. 6 (base:Sub>A).
In fig. 8, the crank angle range of 0 ° to 180 ° shown by hatching indicates the space on the suction side where the low-temperature refrigerant gas exists, and the flow path 82 is provided in the crank angle range of 180 ° to 360 ° so that the flow paths provided in the space in the partition plate 68 in this range do not overlap in the axial direction of the rotary shaft 53.
In fig. 8, the refrigerant gas discharged to the lower side through the first partition plate discharge port 81 passes through a flow path 82 indicated by a broken line, and is discharged into a space above the main bearing 61 through a discharge path 87 provided in parallel with a bolt hole penetrating from one end face to the other end face of the upper cylinder tube 60.
The refrigerant gas discharged to the main bearing 61 has a high temperature, but the portion of the main bearing 61 overlapping the suction-side space has a constant thickness and is sufficiently thicker than the portion of the partition plate 68 having the flow passage 82, and therefore the heat of the high-temperature refrigerant gas is less likely to be transmitted into the upper cylinder tube 60. The space above the main bearing 61 is larger than the space inside the partition plate 68, and the temperature of the refrigerant gas does not decrease significantly even if heat is transferred into the upper cylinder 60.
The first bearing discharge port 80 provided in the main bearing 61, the second bearing discharge port provided in the lower bearing 71, the first partition plate discharge port 81 provided continuously with the space in the upper cylinder 60 of the partition plate 68, and the second partition plate discharge port provided continuously with the space in the lower cylinder 70 of the partition plate 68 can all have the same diameter.
However, since the refrigerant gas discharged from the first and second partition plate discharge ports 81 and 87 is discharged to the space above the main bearing 61 through the flow path provided in the space in the partition plate 68 and the discharge path with the same diameter, a pressure loss occurs, the ratio of the refrigerant gas having a decreased pressure increases, and the discharge pressure as a whole decreases.
Therefore, the diameters of the first partition plate discharge port 81 and the second partition plate discharge port can be made smaller than the diameters of the first bearing discharge port 80 and the second bearing discharge port. This increases the amount of the refrigerant gas discharged from the first bearing discharge port 80 and the second bearing discharge port, and thus can suppress a decrease in the discharge pressure as a whole.
Fig. 9 is a diagram showing a third configuration example of the compressor. The main structure of the compressor 30 is the same as that shown in fig. 6 (a). Fig. 9 isbase:Sub>A sectional view taken at the same position as the cutting linebase:Sub>A-base:Sub>A in fig. 6 (base:Sub>A).
As shown in fig. 9, the diameter of the first partition plate discharge port 81 is smaller than the diameter of the first bearing discharge port 80. Although not shown, the diameter of the discharge port of the second partition plate is also smaller than the diameter of the discharge port of the second bearing. Provided that the diameters D of the first and second partition plate discharge openings 81 and 81 1 Is larger than the diameters D of the first bearing discharge port 80 and the second bearing discharge port 2 Small, i.e. of any size, e.g. D 1 Can be set to 0.5D 2 ～0.95D 2 。
The first bearing discharge port 80, the second bearing discharge port, the first partition plate discharge port 81, and the second partition plate discharge port can have any diameters.
However, if the diameters of the first partition plate discharge port 81 and the second partition plate discharge port are larger than the width of the end face of the roller 62, that is, the width of the flat planar portion of the roller 62 in the axial direction of the rotary shaft 53, which is in contact with the front and back planar portions of the partition plate 68, the first partition plate discharge port 81 and the second partition plate discharge port cannot be completely closed by the roller 62.
Since the first and second partition plate discharge ports 81 and 70 are provided at positions along the inner surfaces of the upper and lower cylinders 60 and 70, if the width of the port is larger than the width of the end surface of the roller 62, the space on the suction side (low pressure side) and the space on the discharge side (high pressure side) partitioned by the roller 62 and the vane 63 are connected to each other, and cannot be compressed to a desired pressure.
Therefore, the diameters of the first partition plate discharge port 81 and the second partition plate discharge port can be made smaller than the width of the flat surface portion of the end surface of the roller 62. Thus, the first and second separator discharge ports 81 and 62 are connected to the high-pressure side space and exposed to the low-pressure side space as the rollers 62 move, but are completely closed by the rollers 62 during this time, so that the connection between the two spaces can be prevented.
Fig. 10 is a diagram showing a fourth configuration example of the compressor. The main structure of the compressor 30 is the same as that shown in fig. 6 (a). Fig. 10 (base:Sub>A) isbase:Sub>A cross-sectional view taken at the same position as the cutting linebase:Sub>A-base:Sub>A in fig. 6 (base:Sub>A), and fig. 10 (b) is an enlarged view showingbase:Sub>A portion surrounded by the range D in fig. 10 (base:Sub>A).
As shown in FIG. 10 (b), the diameter D of the discharge port 81 of the first partition plate 1 Is smaller than the width W of the flat surface portion of one end surface of the roller 62. The diameter of the discharge port of the second partition plate is also D 1 And is smaller than the width W of the flat surface portion of the other end surface of the roller 62. Diameter D of the first and second partition plate discharge ports 81 and 81 1 Any size, D, may be used as long as it is smaller than the width W 1 For example, 0.5W to 0.95W can be set.
Thus, the description has been given of the case where the main bearing 61 is provided with the single first bearing discharge port 80, the lower bearing 71 is provided with the single second bearing discharge port, and the partition plate 68 is provided with the first partition plate discharge port 81 and the second partition plate discharge port. However, the number of these discharge ports is not limited to these numbers. Therefore, two or more first bearing discharge ports 80 may be provided in the main bearing 61, or two or more second bearing discharge ports may be provided in the lower bearing 71. Two or more first partition plate discharge ports may be provided in the partition plate 68, or two or more second partition plate discharge ports may be provided.
Fig. 11 is a diagram showing a fifth configuration example of the compressor 30. The main structure of the compressor 30 is the same as that shown in fig. 6 (a). Fig. 11 (base:Sub>A) isbase:Sub>A sectional view taken at the same position as the cutting linebase:Sub>A-base:Sub>A of fig. 6 (base:Sub>A), fig. 11 (B) isbase:Sub>A sectional view taken by the cutting line B-B in fig. 11 (base:Sub>A), and fig. 11 (C) isbase:Sub>A sectional view taken by the cutting line C-C in fig. 11 (base:Sub>A).
In the example shown in fig. 11, one first bearing discharge port 80 and two first partition plate discharge ports 81 are provided. The first bearing discharge port 80 is provided at about 350 crank angle degrees. One reference numeral 81a of the first partition plate discharge port 81 is provided at a position near the crank angle of 270 °, and the other reference numeral 81b is provided at a position near the crank angle of 350 °. Therefore, the first bearing discharge port 80 and the first partition plate discharge port 81b are coaxially provided in the vicinity of the crank angle of 350 °.
If the discharge path is extended in two and the two paths are coaxially arranged, there is a problem that a sufficient discharge force for opening the discharge valve cannot be obtained when the flow rate is small after the crank angle is 270 °. However, when the discharge paths are expanded into three and two of them are provided coaxially as in the example shown in fig. 11, since there is originally a sufficient flow rate that can be discharged from the three discharge paths, it is possible to secure a sufficient discharge force to open the discharge valve even when the flow rate decreases after the crank angle is 270 ° unlike the case where the discharge paths are simply expanded into two and provided coaxially.
Therefore, if the one first bearing discharge port 80 and the one first partition plate discharge port 81 are disposed offset so as not to overlap in the axial direction of the rotating shaft 53, the other first bearing discharge port 80 and the one first partition plate discharge port 81, or the one first bearing discharge port 80 and the other first partition plate discharge port 81 may be disposed coaxially.
By increasing the number of discharge ports in this manner, the discharge path can be enlarged, and a large capacity can be handled.
As described above, two discharge ports can be provided to enlarge the discharge path, but they are not arranged coaxially but are arranged offset from each other, so that even in a section (crank angle) where the space on the high-pressure side in the cylinder decreases and the discharge flow rate decreases, the area of the discharge path can be changed to secure a predetermined jet flow force. This can suppress pressure loss and improve the performance of the compressor.
The compressor and the heat exchange system of the present invention have been described in detail with reference to the above embodiments, but the present invention is not limited to the above embodiments, and other embodiments, additions, modifications, deletions, and the like can be modified within the scope of the knowledge of those skilled in the art, and any embodiments are included within the scope of the present invention as long as the functions and effects of the present invention are achieved.
Claims (8)
1. A compressor having a plurality of compression mechanisms, the compressor being characterized in that,
each of the compression mechanisms includes:
a hollow cylindrical body having a suction path for sucking a refrigerant;
a rotating body that eccentrically rotates by rotation of a rotating shaft disposed at the center in the cylindrical body;
a separation unit that is in contact with an outer peripheral surface of the rotating body and separates the cylindrical body into two spaces;
a first covering member that has a first discharge path and covers one end of the cylindrical body in the axial direction of the rotating shaft;
a first discharge valve that is provided so as to close the first discharge path, and that is lifted by the refrigerant compressed by the rotation of the rotating body, and discharges the refrigerant;
a second covering member that has a second discharge path and covers the other end of the cylindrical body in the axial direction of the rotating shaft; and
a second discharge valve provided so as to close the second discharge path and lifted by the refrigerant compressed by the rotation of the rotary body to discharge the refrigerant,
the first discharge path and the second discharge path are displaced by a predetermined distance or more from each other in a direction perpendicular to the axial direction.
2. Compressor in accordance with claim 1,
the plurality of compression mechanisms includes a first compression mechanism and a second compression mechanism,
the first compression mechanism includes a first bearing as the first cover member, a first cylinder as the cylindrical body, and a partition plate as the second cover member,
the second compression mechanism includes a second bearing as the first cover member, a second cylinder as the cylindrical body, and the partition plate as the second cover member.
3. The compressor of claim 2,
the first bearing has a first bearing discharge path as the first discharge path,
the second bearing has a second bearing discharge path as the first discharge path,
the partition plate has a first partition plate discharge path and a second partition plate discharge path as the second discharge path,
the first bearing discharge path and the first partition discharge path are provided along an inner periphery of the first cylinder,
the second bearing discharge path and the second partition discharge path are provided along the inner periphery of the second cylinder,
the first bearing discharge path and the second bearing discharge path are provided at positions having a crank angle of 220 DEG to 300 DEG, which is determined by the positions at which the rotating body contacts the inner circumferential surfaces of the first cylinder and the second cylinder,
the first partition plate discharge path and the second partition plate discharge path are provided at positions where the crank angle is 330 ° to 355 °.
4. The compressor of claim 3,
the partition plate has a first flow path and a second flow path through which the refrigerant discharged from the first discharge valve and the second discharge valve flows,
the first flow path and the second flow path are arranged so as not to overlap in the axial direction a space continuous with each suction path among two spaces formed in the first cylinder and the second cylinder, respectively.
5. The compressor of claim 3,
the diameters of the first and second bearing discharge paths are smaller than the diameters of the first and second partition plate discharge paths.
6. The compressor according to any one of claims 3 to 5,
a first rotating body that rotates in the first cylinder and a second rotating body that rotates in the second cylinder have end faces that face in the axial direction,
the diameters of the first and second partition plate discharge paths are smaller than the width of the end surface.
7. A compressor having a plurality of compression mechanisms, the compressor being characterized in that,
each of the compression mechanisms includes:
a hollow cylindrical body having a suction path for sucking a refrigerant;
a rotating body that eccentrically rotates by rotation of a rotating shaft disposed at the center in the cylindrical body;
a separation unit that is in contact with an outer peripheral surface of the rotating body and separates the cylindrical body into two spaces;
a first covering member that has one or more first discharge paths and covers one axial end of the cylindrical body;
a first discharge valve that is provided so as to close the first discharge path, and that is lifted by the refrigerant compressed by the rotation of the rotating body, and discharges the refrigerant;
a second covering member that has one or more second discharge paths and covers the other end of the cylindrical body in the axial direction of the rotating shaft; and
a second discharge valve provided so as to close the second discharge path and lifted by the refrigerant compressed by the rotation of the rotary body to discharge the refrigerant,
each position of at least one of the one or more first discharge paths and at least one of the one or more second discharge paths is deviated by a predetermined distance or more from each other in a direction perpendicular to the axial direction for each of the tubular bodies.
8. A heat exchange system, characterized in that,
comprising the compressor according to any one of claims 1 to 7, and circulating a refrigerant by the compressor to perform heat exchange.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2021128354A JP7003319B1 (en) | 2021-08-04 | 2021-08-04 | Compressor and heat exchange system |
| JP2021-128354 | 2021-08-04 |
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| Publication Number | Publication Date |
|---|---|
| CN115875232A true CN115875232A (en) | 2023-03-31 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202210798896.7A Pending CN115875232A (en) | 2021-08-04 | 2022-07-06 | Compressor and heat exchange system |
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| JP (1) | JP7003319B1 (en) |
| CN (1) | CN115875232A (en) |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006118421A (en) * | 2004-10-21 | 2006-05-11 | Matsushita Electric Ind Co Ltd | Hermetic rotary compressor |
| JP6374732B2 (en) * | 2014-08-29 | 2018-08-15 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle apparatus |
| WO2016076064A1 (en) * | 2014-11-10 | 2016-05-19 | 東芝キヤリア株式会社 | Rotating compressor and refrigeration cycle device |
| JP2019132254A (en) * | 2018-02-02 | 2019-08-08 | 東芝キヤリア株式会社 | Rotary compressor and refrigeration cycle device |
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2021
- 2021-08-04 JP JP2021128354A patent/JP7003319B1/en active Active
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| JP7003319B1 (en) | 2022-01-20 |
| JP2023023120A (en) | 2023-02-16 |
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