Compressor and heat exchange system

Abstract

This invention provides a compressor and heat exchange system capable of ensuring sufficient jet force to open the discharge valve and reducing pressure loss. The compressor comprises multiple compression mechanisms, including: a cylinder (60) having a refrigerant intake path; a roller (62) that rotates eccentrically by rotation of a rotating shaft; blades (63) that abut against the outer circumferential surface of the roller (62) and separate the cylinder (60) into two spaces; a bearing having a bearing discharge port (80); a discharge valve configured to block the bearing discharge port (80) and discharge refrigerant compressed by rotation of the roller (62); a partition plate (68) having a partition plate discharge port (81); and a discharge valve configured to block the partition plate discharge port (81) and discharge refrigerant compressed by rotation of the roller (62). The bearing discharge port (80) and the partition plate discharge port (81) are each offset by a certain distance in a direction perpendicular to the axial direction.

Description

Technical Field

[0001] This invention relates to a compressor having multiple compression mechanisms and a heat exchange system. Background Technology

[0002] In heat exchange systems such as air conditioning units, rotary compressors are used to compress refrigerant and circulate it within the system. A rotary compressor, as a compression mechanism, includes a hollow cylindrical body (cylinder) and a rotating body (roller) that rotates within the cylinder. The refrigerant gas drawn into the cylinder is compressed by the rotation of the roller within the cylinder.

[0003] The rotary compressor has two compression mechanisms. One cylinder has its upper side sealed by a main bearing and its lower side sealed by a partition plate to form a compression chamber. The other cylinder has its upper side sealed by the same partition plate and its lower side sealed by a lower bearing to form another compression chamber. In this configuration, the refrigerant gas compressed in each compression chamber is discharged through discharge paths located on the main bearing and the lower bearing, respectively.

[0004] To increase the compressor's output capacity without making its size too large, thus achieving a larger capacity, the cross-sectional area of ​​the discharge path orifice can be increased to widen the discharge path. However, simply increasing the cross-sectional area of ​​one orifice will cause the discharge valve located in the discharge path to deform due to the increased stress caused by the pressure difference between the inside and outside of the compressor chamber when it is pressed into the compressor chamber, thus reducing its reliability.

[0005] Therefore, a compressor is proposed in which a discharge path is also provided on the partition plate separating the upper and lower compression chambers, and one compression chamber has two discharge paths (for example, see Patent Document 1). In this compressor, the angle between the straight line connecting the rotation axis that rotates the roller and the position where the roller contacts the cylinder wall and the direction of the blade extending from the contact roller and dividing the compression chamber into two is defined as the crank angle. The discharge path provided on the partition plate is located at approximately the same crank angle of 350° as the discharge path provided on the main bearing and the lower bearing.

[0006] Prior art literature

[0007] Patent documents

[0008] Patent Document 1: Japanese Patent No. 6022247 Summary of the Invention

[0009] The problem that the invention aims to solve

[0010] The discharge valves located in each discharge path are opened by the jet force of the refrigerant gas flowing into the discharge path. As the crank angle approaches 350°, the orifice of the discharge path connected to the compression chamber is closed by the roller, and the flow rate gradually decreases. However, in a structure with one discharge path for each compression chamber, sufficient jet force can be obtained even when the crank angle exceeds 270°.

[0011] However, in the existing technology described above, the flow rate is distributed equally to both discharge paths during one revolution of the roller, and the flow rate of each discharge path is reduced. Therefore, if the crank angle exceeds 270°, it is not possible to obtain a jet force sufficient to open the discharge valve, and the discharge becomes from a smaller gap, resulting in a problem of increased pressure loss.

[0012] Solution for solving the problem

[0013] In view of the above-mentioned problems, the present invention provides a compressor having multiple compression mechanisms, characterized in that,

[0014] Each compression mechanism includes:

[0015] A hollow cylindrical body with an intake path for drawing in refrigerant;

[0016] A rotating body that rotates eccentrically by rotating a rotation axis located at the center of the cylindrical body;

[0017] The separation unit abuts against the outer peripheral surface of the rotating body, dividing the cylindrical body into two spaces.

[0018] A first covering component has a first discharge path and covers one end of the axial direction of the rotation axis of the cylindrical body;

[0019] The first discharge valve is configured to block the first discharge path and is lifted by the refrigerant compressed by the rotation of the rotating body, so that the refrigerant is discharged.

[0020] A second covering member, having a second discharge path, covers the other end of the axial direction of the rotation axis of the cylindrical body; and

[0021] The second discharge valve is configured to block the second discharge path and is lifted by the refrigerant compressed by the rotation of the rotating body, causing the refrigerant to be discharged.

[0022] The positions of the first and second ejection paths in the direction perpendicular to the axis are deviated by a certain distance.

[0023] Invention Effects

[0024] According to the present invention, a compressor and heat exchange system can be provided that can ensure sufficient jet force to open the discharge valve and reduce pressure loss. Attached Figure Description

[0025] Figure 1 This is a diagram showing an example of the structure of an air conditioning unit as an example of a heat exchange system.

[0026] Figure 2 This is a diagram illustrating the refrigerant circuit of an air conditioning unit.

[0027] Figure 3 This is a diagram showing the main components of the compressor in an outdoor unit.

[0028] Figure 4 This is a diagram showing an example of the structure of an electric motor.

[0029] Figure 5 This is a diagram showing an example of the structure of a compression mechanism.

[0030] Figure 6 This is a diagram showing a first structural example of a compressor.

[0031] Figure 7 This diagram illustrates the valve operation when the position of the orifice in the discharge path of the partition plate is changed.

[0032] Figure 8 This is a diagram showing a second structural example of a compressor.

[0033] Figure 9 This is a diagram showing an example of the third structure of a compressor.

[0034] Figure 10 This is a diagram showing the fourth structural example of a compressor.

[0035] Figure 11 This is a diagram showing the fifth structural example of a compressor.

[0036] In the picture:

[0037] 10—Air conditioning unit; 11—Indoor unit; 12—Outdoor unit; 13—Remote control; 20—Indoor heat exchanger; 21—Indoor fan; 22—Drive motor for indoor fan; 30—Compressor; 31—Receiver; 32—Four-way valve; 33—Expansion valve; 34—Outdoor heat exchanger; 35—Outdoor fan; 36—Drive motor for outdoor fan; 37—Control device; 40—Housing; 41—Upper cover; 42—Lower cover; 43—Suction pipe; 44—Seal; 45—Discharge pipe; 46—Motor; 47—Compression mechanism; 50—Stator; 51—Rotor; 52—Wire; 53—Rotation Shaft, 54—eccentric cam, 55—blade, 56—oil supply component, 60—upper cylinder, 61—main bearing, 62—roller, 63—blade, 64—spring, 65—discharge valve, 66—retainer, 67—upper discharge cover, 68—partition plate, 70—lower cylinder, 71—lower bearing, 72—roller, 73—blade, 74—spring, 75—discharge valve, 76—retainer, 77—lower discharge cover, 80—first bearing discharge outlet, 81, 81a, 81b—first partition plate discharge outlet, 82—flow path, 83, 84—discharge valve, 85, 86—retainer, 87—discharge path. Detailed Implementation

[0038] The heat exchange system of this embodiment is a system that allows heat exchange between a fluid and a refrigerant. It circulates the refrigerant within a closed system, heating or cooling the drawn-in fluid through heat exchange with the circulating refrigerant, and then discharging it. The fluid can 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 for heating or cooling the refrigerant within the system. Examples of such heat exchange systems with compressors, heat exchangers, and expansion valves include air conditioning units, coolers (cooling water circulation devices), and refrigeration units.

[0039] Figure 1 This diagram illustrates a structural example of an air conditioning unit. Here, the heat exchange system is described as an air conditioning unit. The air conditioning unit 10 includes an indoor unit 11 located in the space where air conditioning is performed (indoors), an outdoor unit 12 located outdoors, and a remote control 13 operated by the user. Refrigerant circulates between the indoor unit 11 and the outdoor unit 12, exchanging heat with the indoor air, thereby achieving air conditioning. Therefore, the indoor unit 11 and the outdoor unit 12 are connected by two refrigerant pipes 14 and 15 for refrigerant circulation.

[0040] The indoor unit 11 and the outdoor unit 12 can each consist of two or more units, or two or more indoor units 11 can be connected to one outdoor unit 12. As a refrigerant, hydrofluorocarbons (HFCs) can be used, and examples of HFCs include R-410A and R-32.

[0041] The indoor unit 11 communicates wirelessly with the remote control 13 using infrared or similar methods, receiving various signals such as operation commands, stop commands, temperature setting change commands, and operation mode change commands. The indoor unit 11 is connected to the outdoor unit 12 via a communication cable, and works with the outdoor unit 12 to regulate the indoor air.

[0042] The indoor unit 11 starts upon receiving an operation command from the remote control 13 and instructs the outdoor unit 12 to start as well. After starting, the outdoor unit 12 adjusts the compressor speed, the opening of the expansion valve, and controls the refrigerant circulation to ensure that the indoor temperature reaches the set temperature.

[0043] Reference Figure 2 The refrigerant circuit of the air conditioning unit 10 will be briefly described. Figure 2 The arrows shown indicate the flow of refrigerant during cooling operation, and the explanation focuses on the operation during cooling. Furthermore, during heating operation, the refrigerant flows in the opposite direction.

[0044] 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, driven by the indoor fan drive motor 22, draws in indoor air and delivers it to the indoor heat exchanger 20. The indoor heat exchanger 20 has internal heat-conducting pipes for refrigerant circulation, and the delivered air exchanges heat with the surface of the heat-conducting pipes. The air that has undergone heat exchange through the indoor heat exchanger 20 is then discharged into the room.

[0045] In addition, the indoor unit 11 can also be equipped with various sensors, expansion valves, etc. for measuring indoor temperature.

[0046] The outdoor unit 12 includes a compressor 30, a receiver 31, a four-way valve 32, an expansion valve 33, an outdoor heat exchanger 34, an outdoor fan 35, and a drive motor 36 for the outdoor fan. The compressor 30, driven by the compressor drive motor, compresses low-pressure gaseous refrigerant and discharges it as high-pressure gaseous refrigerant. The receiver 31 is a container for storing liquid return during transition, adjusting the refrigerant to a suitable dryness level. Dryness level indicates the proportion of vapor in a mixture of vapor and tiny liquid droplets in wet vapor.

[0047] The four-way valve 32 is a valve that switches the refrigerant flow path according to the operating state (operating mode) of the air conditioning unit 10. Operating modes include cooling mode, heating mode, and fan-only mode. The expansion valve 33 is a valve that reduces the pressure of the high-pressure refrigerant and causes it to expand. The outdoor fan 35 is driven by the outdoor fan drive motor 36, drawing in outdoor air and sending it into the outdoor heat exchanger 34. Like the indoor heat exchanger 20, the outdoor heat exchanger 34 has internal heat-conducting pipes for refrigerant flow; the incoming air contacts the surface of the heat-conducting pipes for heat exchange. The air that has undergone heat exchange through the outdoor heat exchanger 34 is discharged outdoors.

[0048] The outdoor unit 12 includes a control device 37. The control device 37 is connected to the compressor 30, four-way valve 32, expansion valve 33, indoor fan drive motor 22, and outdoor fan drive motor 36, and controls them. Specifically, it controls the speed of the compressor 30, the opening degree of the expansion valve 33, and the speeds of the indoor fan drive motor 22 and the outdoor fan drive motor 36. Various sensors are also installed on the outdoor unit 12 for controlling these components. The control device 37 controls these components based on information detected by these sensors.

[0049] During refrigeration operation, the indoor heat exchanger 20 is used as an evaporator, and the outdoor heat exchanger 34 is used as a condenser. Therefore, the control device 37, as indicated by the arrow, causes the refrigerant sealed in the system to circulate in the following order: compressor 30, outdoor heat exchanger 34, expansion valve 33, indoor heat exchanger 20, four-way valve 32, receiver 31, and compressor 30.

[0050] The compressor 30 compresses the refrigerant (refrigerant gas) in a low-temperature, low-pressure gaseous state and discharges it as a high-temperature, high-pressure refrigerant gas. The outdoor heat exchanger 34 exchanges heat with the outdoor air, cooling the refrigerant gas and causing it to condense. The expansion valve 33 depressurizes the refrigerant and partially vaporizes it. Therefore, the refrigerant is supplied to the indoor unit 11 in a gas-liquid mixture. The opening of the expansion valve 33 is adjusted by the control device 37 to achieve the appropriate amount of liquid.

[0051] The indoor heat exchanger 20 exchanges heat with the indoor air, and the condensed liquid refrigerant is completely vaporized and returned to the outdoor unit 12 as refrigerant gas. The refrigerant gas returning from the indoor heat exchanger 20 is transported to the receiver 31 through the four-way valve 32 and then returned to the compressor 30.

[0052] The control device 37 is installed on the outdoor unit 12, but is not limited to it. It can also be installed on the indoor unit 11, or on other central control panels, etc.

[0053] The heat exchange system can employ a rotary compressor as compressor 30. A rotary compressor is a compressor that compresses refrigerant through a combination of a hollow cylindrical body (cylinder) and a rotating body (roller). The cylindrical body has an intake path for drawing in refrigerant, and the rotating body rotates eccentrically by the rotation of a rotating shaft located at the center of the cylinder.

[0054] Reference Figure 3 The main components of the compressor 30 in the outdoor unit 12 will be described below. The compressor 30 includes a hollow cylindrical housing 40, an upper cover 41 covering the upper part of the housing 40, and a lower cover 42 covering the lower part of the housing 40, forming a sealed space. A suction pipe 43 is provided in the housing 40, which is connected to a liquid receiver 31 via a seal 44, and draws refrigerant gas from the liquid receiver 31 during cooling operation. A discharge pipe 45 is provided in the upper cover 41, which supplies the refrigerant gas compressed by the compressor 30 to the outdoor heat exchanger 34 during cooling operation.

[0055] The compressor 30 is housed within a space enclosed by the housing 40, the upper cover 41, and the lower cover 42. An electric motor 46 and a compression mechanism 47, which constitute the compressor 30, are used to draw in and compress refrigerant gas. In this example, the compression mechanism 47 is configured with two layers. The compressed refrigerant gas is discharged into the space between the electric motor 46 and the upper compression mechanism 47, and into the space between the lower compression mechanism 47 and the lower cover 42. It is also transported through the gaps between the compression mechanism 47, the electric motor 46, and the housing 40 to the space between the electric motor 46 and the upper cover 41, and discharged from the discharge pipe 45 located on the upper cover 41.

[0056] Reference Figure 4 The structure of the electric motor 46 will be described in detail below. The electric motor 46 includes a stator 50 and a rotor 51. The stator 50 has coils, to which wires 52 for supplying current are connected. The rotor 51 is a permanent magnet or the like, which rotates by the flow of current through the coils.

[0057] A hole of a predetermined diameter is formed in the center of the rotor 51, into which the rotating shaft 53 can be inserted and mounted. An eccentric cam 54 is provided on the outer periphery of the rotating shaft 53 in a manner that allows the roller to rotate eccentrically. Here, the compression mechanism 47 is provided in two layers, with rollers in both layers, and therefore the eccentric cam 54 is provided in two layers.

[0058] The rotating shaft 53 has a cavity extending axially from its lower end. Within this cavity are blades 55 and an oil supply unit 56 for drawing refrigerant oil filled between the lower cover 42 and the lower compression mechanism 47 and supplying it to sliding parts such as between the cylinder and rollers. The refrigerant oil has high lubricity and is supplied to reduce wear on the sliding parts. Furthermore, the refrigerant oil is discharged from the compression mechanism 47 along with refrigerant gas and therefore needs to return to the stored lower cover 42, exhibiting a degree of refrigerant compatibility. Additionally, the refrigerant oil discharged along with the refrigerant gas onto the compression mechanism 47 is in a mist form, falling onto the inclined compression mechanism 47, flowing on this inclined surface, and falling through a discharge hole communicating with the lower cover 42 located at the edge of the compression mechanism 47, returning to the lower cover 42.

[0059] Reference Figure 5 The structure of the compression mechanism 47 is described in detail. Figure 5 The diagram shows an example of a two-layer compression mechanism 47. The upper compression mechanism consists of an upper cylinder 60, a main bearing 61, a roller 62, a blade 63, a spring 64, a discharge valve 65, a discharge valve retainer (retainer) 66, an upper discharge cover 67, and a partition plate 68.

[0060] The lower compression mechanism consists of a lower cylinder 70, a lower bearing 71, a roller 72, a blade 73, a spring 74, a discharge valve 75, a retainer 76, a lower discharge cover 77, and a partition plate 68. Furthermore, the partition plate 68 separates the upper and lower layers, and is therefore used in both compression mechanisms. The structure and operation of the lower compression mechanism are the same as those of the upper compression mechanism; therefore, only the upper compression mechanism will be described here.

[0061] The upper cylinder 60 is a hollow cylindrical body with grooves and holes to accommodate the blade 63 and spring 64, which function as a separation unit. A hollow cylindrical roller 62 is housed inside the upper cylinder 60. One end of the blade 63 abuts against the outer circumferential surface of the roller 62, and the other end engages with the spring 64, maintaining its pressure against the roller 62. The spring 64 is configured such that one end engages with the other end of the blade 63, and the other end abuts against the inner surface of the housing 40.

[0062] An eccentric cam 54 with a rotating shaft 53 is inserted into roller 62. Roller 62 rotates eccentrically within upper cylinder 60 by the rotation of rotating shaft 53. Blade 63 maintains contact with the outer circumferential surface of roller 62 while separating the upper cylinder 60 into two spaces. Upper cylinder 60 has a continuous suction path to one of the two spaces separated by blade 63, supplying refrigerant gas drawn in from suction pipe 43.

[0063] The main bearing 61 and the lower bearing 71 are rotatably supported on the rotating shaft 53. The main bearing 61 covers one side of the axial direction of the rotating shaft 53 of the upper cylinder 60 and has a discharge path for discharging compressed refrigerant gas. A discharge valve 65 is located in the discharge path and is lifted by the jet force of the refrigerant gas, discharging refrigerant gas through this gap into the space on the main bearing 61. An upper discharge cover 67 is disposed on the main bearing 61 and functions as a muffler to reduce the noise emitted by the discharged refrigerant gas. The discharge valve 65, lifted by the jet force of the refrigerant gas, is held in shape in a non-deformable manner by a retainer 66. The discharge valve 65 can return to its original position and block the discharge path when the jet force of the refrigerant gas decreases, thanks to the retainer 66.

[0064] The partition plate 68 covers the other side of the axial direction of the rotation shaft 53 of the upper cylinder 60 and has a discharge path for discharging compressed refrigerant gas. A discharge valve and a retainer are also provided in this discharge path. The discharge valve is lifted by the jet force of the refrigerant gas, discharging the refrigerant gas through the gap into the space within the partition plate 68. The space within the partition plate 68 connects to a discharge path located on the edge of the upper cylinder 60 along with bolt holes, through which the refrigerant gas is discharged to the space between the upper cylinder 60 and the upper discharge cover 67.

[0065] This explains the case where two discharge paths are set for one compression chamber, namely, the main bearing 61 and the partition plate 68, and the lower bearing 71 and the partition plate 68. The location of the two discharge paths will be explained below.

[0066] Figure 6 This is a diagram showing a first structural example of a compressor. Figure 6 (a) indicates a reference. Figures 3-5 A diagram illustrating the structure of compressor 30. Figure 6 (b) is Figure 6 The sectional view cut by cutting line AA in (a). Figure 6 (c) is Figure 6 The sectional view cut by cutting line BB in (b). Figure 6 (d) is an enlarged representation. Figure 6 The part of the graph represented by region C in (c).

[0067] like Figure 6 As shown in (b), within the upper cylinder 60, the roller 62 rotates eccentrically, and one end of the blade 63 abuts against the outer circumferential surface of the roller 62. The upper cylinder 60 has bolt holes and the like at its edge, and has a groove that is continuous with the internal space and accommodates the blade 63. The blade 63 slides within the groove while maintaining one end abutting against the outer circumferential surface of the roller 62.

[0068] exist Figure 6 In (b), in the horizontal direction perpendicular to the axial direction of the rotation axis 53, the direction in which the blade 63 extends is set to a crank angle of 0°, and the discharge path (first bearing discharge port) 80 of the main bearing 61 exists at a position near a crank angle of 350° along the inner surface of the upper cylinder 60. Furthermore, the refrigerant gas intake path is formed to be continuous with the space (intake side space) formed on the side opposite to the first bearing discharge port 80 via the blade 63.

[0069] exist Figure 6 In (b), the position of the discharge path (first partition plate discharge port) 81 of the partition plate 68 in the vertical direction perpendicular to the axis of rotation 53 is deviated from the position of the first bearing discharge port 80 in the vertical direction by a certain distance, and exists at a position along the inner surface of the upper cylinder 60 and near the crank angle 270°.

[0070] like Figure 6 As shown in (d), the first partition plate outlet 81 is continuous with the flow path 82 of the space provided within the partition plate 68. Discharge valves 83 and 84 and retainers 85 and 86 are similarly provided in the partition plate 68 and the main bearing 61. Therefore, by utilizing the jet force of the refrigerant gas to open the discharge valves 83 and 84, refrigerant gas is discharged into the flow path 82. The refrigerant gas discharged into the flow path 82 is discharged through the discharge path to the space on the main bearing 61, and further moves through the gap between the motor 46 and the housing 40 to the space between the motor 46 and the upper cover 41, and is discharged from the discharge pipe 45.

[0071] The discharge gas flow rate of the rotary compressor decreases as the crank angle approaches 360°. For example, when roller 62 is at a crank angle of 180°, the space on the low-pressure side, where the suction path exists, is separated by blade 63 into the space on the high-pressure side, where the first bearing discharge port 80 and the first partition plate discharge port 81 exist. By rotating eccentrically, roller 62 moves from a crank angle of 180° to 360° while its outer circumferential surface contacts the inner surface of the upper cylinder 60. This movement reduces the space on the high-pressure side, thus decreasing the discharge gas flow rate.

[0072] In the high-pressure side, where the crank angle is between 180° and 270°, the space is large and the flow rate of the discharged gas is high. Even if the horizontal position of the first partition plate outlet 81 and the horizontal position of the first bearing outlet 80 are approximately the same, the pressure loss can be reduced by discharging gas from both outlet ports.

[0073] However, when the crank angle exceeds 270°, the space on the high-pressure side becomes smaller, and the flow rate of the discharged gas decreases. Because it is distributed to two discharge ports, the flow rate at each discharge port becomes too small. The force pushing up the discharge valve 65 is insufficient, resulting in discharge from the smaller flow path and increasing pressure loss. If the pressure loss increases, the desired flow rate cannot be obtained, affecting performance.

[0074] like Figure 6 As shown in (b), the first partition plate outlet 81 and the first bearing outlet 80 are not positioned coaxially, but rather offset. This allows for discharge from both outlets (first bearing outlet 80 and first partition plate outlet 81) in areas with high flow rates, while discharge from only outlet (first bearing outlet 80) occurs in areas where the crank angle is close to 350° and the flow rate decreases. This prevents the flow rate from becoming too low, thus reducing the force required to push the discharge valve upwards and suppressing an increase in pressure loss.

[0075] Specifically, the first bearing outlet 80 is positioned near a crank angle of 350°, and the first partition plate outlet 81 is positioned near a crank angle of 270°. When the roller 62 is positioned at, for example, a crank angle of 200°, the first partition plate outlet 81 is not blocked by the roller 62, thus allowing discharge from both the first bearing outlet 80 and the first partition plate outlet 81. As the roller 62 approaches the 270° position, the first partition plate outlet 81 is gradually blocked by the roller 62, and when it reaches approximately 270°, the first partition plate outlet 81 is completely blocked. Therefore, discharge only occurs from the first bearing outlet 80.

[0076] Subsequently, as roller 62 moves, the first partition plate discharge port 81 gradually opens, but it is continuous with the space on the low-pressure side. Since the refrigerant gas is at low pressure, the discharge valve cannot be pushed up, and the refrigerant gas is not discharged.

[0077] Reference Figure 7 The valve operation is explained when the position of the orifice in the discharge path of the partition plate 68 is changed. Figure 7 The left-hand diagram shows an example where the first bearing outlet 80 and the first partition plate outlet 81 are coaxially located around a crank angle of 350°. The central diagram shows an example where the first bearing outlet 80 is located around a crank angle of 350°, but the first partition plate outlet 81 is located around a crank angle of 270°, thus shifting its position. The right-hand diagram shows an example where the first bearing outlet 80 is located around a crank angle of 350°, but the first partition plate outlet 81 is located around a crank angle of 240°, thus shifting its position.

[0078] Regarding valve operation, the crank angle (deg), lift (mm), and flow path area (mm) are shown for the discharge valve during refrigeration operation. 2 The relationship between the two flow paths is shown in the figures. The figures also illustrate the lifting amount and flow path area of ​​the discharge valve 65 on the main bearing 61 side, corresponding to the crank angle, and the lifting amount and flow path area of ​​the discharge valve 83 on the partition plate 68 side. Additionally, the figures also show the parameters for summing the two flow path areas.

[0079] Referring to the diagram on the left, the discharge valve begins to open when the crank angle is around 200°. Around 240°, the lift and flow area are at their maximum. Around 310°, the lift and flow area are approximately zero, and then discharge cease. This is because the first bearing discharge port 80 and the first partition plate discharge port 81 are both located around 350° of the crank angle, effectively distributing two discharge ports. Consequently, after the crank angle reaches 310°, the flow rate at each discharge port becomes too small, resulting in insufficient force to push the discharge valves 65 and 83 upwards.

[0080] Referring to the central diagram, the discharge valve begins to open when the crank angle is around 200°, and the lift and flow area reach their maximum around the crank angle is around 240°. 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 and flow area become zero.

[0081] After the crank angle reaches 270°, since only the first bearing outlet 80 of the main bearing 61 is open, the flow rate will not become too small as shown in the diagram on the left. The discharge valve 65 will open and the refrigerant will be discharged until the crank angle reaches approximately 330°.

[0082] Referring to the diagram on the right, the discharge valve begins to open when the crank angle is around 200°, and the lift and flow area are at their maximum around the crank angle of 240°. In the example shown in the diagram, when the crank angle is around 240°, the first partition plate discharge port 81 of the partition plate 68 is blocked by the roller 62, and the lift and flow area become 0.

[0083] After the crank angle reaches 240°, since only the first bearing outlet 80 of the main bearing 61 is open, the flow rate will not become too small, similar to the example shown in the central figure. The discharge valve 65 opens and refrigerant is discharged until the crank angle is approximately 330°. However, in the example shown in the right-hand figure, the first partition plate outlet 81 is blocked earlier than in the example shown in the central figure. As a result, the period during which the lift and flow path area of ​​the discharge valve 65 on the main bearing 61 side reach their maximum is longer.

[0084] Based on these results, the first bearing outlet 80 can be located near a crank angle of 350° as has always been the case, and the first partition plate outlet 81 can be located at a distance offset from the first bearing outlet 80, such as at a crank angle of 240° or 270°. Furthermore, these outlet locations are examples and are not limited to these locations. For example, the first bearing outlet 80 can be located at a crank angle of 330° to 355°, and the first partition plate outlet 81 can be located at a crank angle of 220° to 300°.

[0085] Furthermore, the high-temperature refrigerant gas flowing into the discharge port 81 of the first partition plate is finally discharged into the sealed housing consisting of the housing 40, the upper cover 41, and the lower cover 42 through the flow path 82 provided in the space within the partition plate 68. When the flow path 82 is provided within the partition plate 68, the thickness of the partition plate 68 separating the space within the upper cylinder 60, the space within the lower cylinder 70, and the flow path 82 is only thinned in the portion of the flow path 82.

[0086] In the case where the flow path 82 is located, for example, below the space on the intake side of the refrigerant gas in the upper cylinder 60 at a crank angle of 0° to 180°, the temperature of the refrigerant gas in the intake side space is low. Therefore, the heat of the high-temperature refrigerant gas flowing in the flow path 82 is transferred to the low-temperature refrigerant gas in the upper cylinder 60 via the partition plate 68, resulting in a decrease in the temperature of the refrigerant gas discharged into the sealed gas. When the temperature of the refrigerant gas decreases, the refrigerant gas may condense. If it condenses and remains, the refrigerant gas will not be discharged.

[0087] Therefore, the flow path 82 can be formed in such a way that the space on the suction side where the low-temperature refrigerant gas exists and the flow path 82 provided in the partition plate 68 do not overlap in the axial direction of the rotation shaft 53.

[0088] Figure 8 This is a diagram showing a second structural example of the compressor. The main structure of compressor 30 is similar to... Figure 6 The structure shown in (a) is the same. Figure 8 In the context of Figure 6 The cross-sectional view cut at the same position as the cutting line AA in (a).

[0089] exist Figure 8 In the diagram, the range of crank angles from 0° to 180°, indicated by shaded lines, represents the space on the suction side where the low-temperature refrigerant gas is present. Flow paths 82 are provided in the range of crank angles from 180° to 360° in such a way that the flow paths in the space provided within the partition plate 68 in this range do not overlap in the axial direction of the rotating shaft 53.

[0090] exist Figure 8The refrigerant gas that is discharged to the lower side through the first partition plate discharge port 81 passes through the flow path 82 shown by the dashed line and is discharged into the space on the main bearing 61 through the discharge path 87 arranged parallel to the bolt hole that runs from one end face of the upper cylinder 60 to the other end face.

[0091] Furthermore, the refrigerant gas discharged onto the main bearing 61 is at a high temperature, but the portion of the main bearing 61 overlapping with the space on the suction side has a certain thickness, which is sufficiently thicker than the portion of the partition plate 68 with the flow path 82. Therefore, the heat from the high-temperature refrigerant gas is difficult to transfer into the upper cylinder 60. The space on the main bearing 61 is larger than the space within the partition plate 68, so even assuming heat transfer into the upper cylinder 60, the temperature of the refrigerant gas will not decrease significantly.

[0092] The holes of the first bearing outlet 80 located in the main bearing 61, the second bearing outlet located in the lower bearing 71, the first partition plate outlet 81 continuously arranged with the space inside the upper cylinder 60 of the partition plate 68, and the second partition plate outlet continuously arranged with the space inside the lower cylinder 70 of the partition plate 68 can all be set to the same diameter.

[0093] However, with the same diameter, the refrigerant gas discharged from the first partition plate outlet 81 and the second partition plate outlet is discharged into the space on the main bearing 61 through the flow path and discharge path 87 provided in the space within the partition plate 68, thus causing pressure loss. The proportion of refrigerant gas with reduced pressure increases, and the overall discharge pressure decreases.

[0094] Therefore, the diameters of the first partition plate outlet 81 and the second partition plate outlet can be smaller than the diameters of the first bearing outlet 80 and the second bearing outlet. As a result, the amount of refrigerant gas discharged from the first bearing outlet 80 and the second bearing outlet increases, which can suppress the decrease in the overall discharge pressure.

[0095] Figure 9 This is a diagram showing a third structural example of a compressor. The main structure of compressor 30 is similar to... Figure 6 The structure shown in (a) is the same. Figure 9 In the context of Figure 6 The cross-sectional view cut at the same position as the cutting line AA in (a).

[0096] like Figure 9 As shown, the diameter of the first partition plate outlet 81 is smaller than the diameter of the first bearing outlet 80. Furthermore, although not shown, the diameter of the second partition plate outlet is also smaller than the diameter of the second bearing outlet. As long as the diameters D1 of the first and second partition plate outlets are smaller than the diameters D2 of the first and second bearing outlets, they can be any size; for example, D1 can be set to 0.5D2 to 0.95D2.

[0097] The first bearing outlet 80, the second bearing outlet, the first partition plate outlet 81, and the second partition plate outlet can be set to any diameter.

[0098] However, if the diameters of the first partition plate outlet 81 and the second partition plate outlet are greater than the width of the end face of the roller 62, that is, the width of the flat plane portion of the roller 62 in contact with the surface and back plane of the partition plate 68 along the axial direction of the rotating shaft 53, then the first partition plate outlet 81 and the second partition plate outlet cannot be completely blocked by the roller 62.

[0099] The first partition plate outlet 81 and the second partition plate outlet are located along the inner surfaces of the upper cylinder 60 and the lower cylinder 70. Therefore, if the width of the end face of the roller 62 is larger than that of the roller 62, the space of the suction side (low pressure side) and the space of the discharge side (high pressure side) separated by the roller 62 and the blade 63 will be connected, and the pressure cannot be compressed to the desired pressure.

[0100] Therefore, the diameters of the first partition plate outlet 81 and the second partition plate outlet can be made smaller than the width of the flat portion of the end face of the roller 62. Thus, as the roller 62 moves, although the first partition plate outlet 81 and the second partition plate outlet are connected to the space on the high-pressure side and exposed to the space on the low-pressure side, they are completely closed by the roller 62 during this period, thus preventing the two spaces from connecting.

[0101] Figure 10 This is a diagram showing the fourth structural example of a compressor. The main structure of compressor 30 is similar to... Figure 6 The structure shown in (a) is the same. Figure 10 (a) is in relation to Figure 6 A cross-sectional view cut at the same position as the cutting line AA in (a). Figure 10 (b) is an enlarged representation. Figure 10 The portion of (a) enclosed by range D.

[0102] like Figure 10 As shown in (b), the diameter D1 of the first partition plate outlet 81 is smaller than the width W of the flat portion of one end face of the roller 62. Similarly, the diameter D1 of the second partition plate outlet is also smaller than the width W of the flat portion of the other end face of the roller 62. The diameters D1 of both the first and second partition plate outlets can be any size as long as they are smaller than the width W; for example, D1 can be set to 0.5W to 0.95W.

[0103] This explains that the main bearing 61 has a first bearing outlet 80, the lower bearing 71 has a second bearing outlet, and the partition plate 68 has a first partition plate outlet 81 and a second partition plate outlet. However, the number of these outlets is not limited to these numbers. Therefore, the main bearing 61 may have two or more first bearing outlets 80, and the lower bearing 71 may have two or more second bearing outlets. Similarly, the partition plate 68 may have two or more first partition plate outlets, and two or more second partition plate outlets.

[0104] Figure 11 This is a diagram showing the fifth structural example of compressor 30. The main structure of compressor 30 is similar to... Figure 6 The structure shown in (a) is the same. Figure 11 (a) is in relation to Figure 6 A cross-sectional view cut at the same position as the cutting line AA in (a). Figure 11 (b) is Figure 11 The sectional view cut by cutting line BB in (a). Figure 11 (c) is Figure 11 The sectional view cut by the cutting line CC in (a).

[0105] exist Figure 11 In the example shown, there is a first bearing outlet 80 and two first partition plate outlets 81. The first bearing outlet 80 is located near a crank angle of 350°. One of the first partition plate outlets 81, denoted by 81a, is located near a crank angle of 270°, and the other, denoted by 81b, is located near a crank angle of 350°. Therefore, near a crank angle of 350°, the first bearing outlet 80 and the first partition plate outlet 81b are coaxially located.

[0106] If the discharge path is expanded to two and placed coaxially, there is a problem that when the flow rate is low beyond 270°, sufficient jet force to open the discharge valve cannot be obtained. However, as Figure 11 As shown in the example, when the discharge path is expanded to three and two of them are set on the same axis, there is already enough flow to be discharged from the three discharge paths. Therefore, unlike the case of simply expanding the discharge path to two and setting them on the same axis, even when the flow decreases after the crank angle is 270°, it is possible to ensure sufficient jet force to open the discharge valve.

[0107] Therefore, if a first bearing outlet 80 and a first partition plate outlet 81 are offset and not overlap in the axial direction of the rotation shaft 53, another first bearing outlet 80 and the first partition plate outlet 81, or the first bearing outlet 80 and the other first partition plate outlet 81, can also be arranged coaxially.

[0108] By increasing the number of discharge outlets, the discharge path can be expanded to cope with larger volumes.

[0109] As explained so far, in order to widen the discharge path, two discharge outlets can be provided, but instead of arranging them coaxially, they are positioned offset from each other. This allows the discharge path area to vary even in areas where the space on the high-pressure side within the cylinder is reduced and the discharge flow rate decreases (crank angle), ensuring the predetermined jet force. This, in turn, suppresses pressure loss and improves compressor performance.

[0110] Thus far, the compressor and heat exchange system of the present invention have been described in detail using the above embodiments. However, the present invention is not limited to the above embodiments. Other embodiments, additions, changes, deletions, etc., can be made within the scope that can be conceived by those skilled in the art. In any way, as long as it achieves the function and effect of the present invention, it is included within the scope of the present invention.

Claims

1. A compressor having multiple compression mechanisms, characterized in that, Each of the compression mechanisms includes: A hollow cylindrical body with an intake path for drawing in refrigerant; A rotating body that rotates eccentrically by rotating a rotation axis disposed at the center of the cylindrical body; A separation unit abuts against the outer peripheral surface of the rotating body, separating the cylindrical body into two spaces. A first covering component has a first discharge path and covers one end of the axial direction of the rotation axis of the cylindrical body; A first discharge valve is configured to block the first discharge path and is lifted by the refrigerant compressed by the rotation of the rotating body, causing the refrigerant to be discharged. The second covering component has a second ejection path and covers the other end of the axial direction of the rotation axis of the cylindrical body; as well as The second discharge valve is configured to block the second discharge path and is lifted by the refrigerant compressed by the rotation of the rotating body, causing the refrigerant to be discharged. The positions of the first and second ejection paths in the direction perpendicular to the axial direction are deviated by a certain distance. 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 covering component, a first cylinder as the cylindrical body, and a partition plate as the second covering component. The second compression mechanism includes a second bearing as the first cover member, a second cylinder as the cylindrical body, and a partition plate as the second cover member. The partition plate has a first flow path and a second flow path for the refrigerant discharged from the first discharge valve and the second discharge valve. The first flow path and the second flow path are configured such that they do not overlap in the axial direction with the spaces that are continuous with each suction path in two spaces formed in the first cylinder and the second cylinder, respectively.

2. The compressor according to claim 1, characterized in that, The first bearing has a first bearing ejection path that serves as the first ejection path. The second bearing has a second bearing ejection path that serves as the first ejection path. The separator plate has a first separator plate ejection path and a second separator plate ejection path, which serve as the second ejection path. The first bearing ejection path and the first partition plate ejection path are arranged along the inner circumference of the first cylinder. The second bearing ejection path and the second partition plate ejection path are arranged along the inner circumference of the second cylinder. The first bearing ejection path and the second bearing ejection path are positioned at crank angles of 220° to 300°, determined by the contact positions between the rotating body and the inner circumferential surfaces of the first and second cylinders, respectively. The first and second partition plate ejection paths are positioned at a crank angle of 330° to 355°.

3. The compressor according to claim 2, characterized in that, The diameters of the first bearing ejection path and the second bearing ejection path are smaller than the diameters of the first partition plate ejection path and the second partition plate ejection path.

4. The compressor according to claim 2 or 3, characterized in that, The first rotating body rotating inside the first cylinder and the second rotating body rotating inside the second cylinder have end faces facing the axial direction. The diameters of the first and second partition plate ejection paths are smaller than the width of the end face.

5. A compressor having multiple compression mechanisms, characterized in that, Each of the compression mechanisms includes: A hollow cylindrical body with an intake path for drawing in refrigerant; A rotating body that rotates eccentrically by rotating a rotation axis disposed at the center of the cylindrical body; A separation unit abuts against the outer peripheral surface of the rotating body, separating the cylindrical body into two spaces. A first covering component has one or more first discharge paths and covers one end of the axial direction of the rotation axis of the cylindrical body; A first discharge valve is configured to block the first discharge path and is lifted by the refrigerant compressed by the rotation of the rotating body, causing the refrigerant to be discharged. The second covering component has one or more second discharge paths and covers the other end of the axial direction of the rotation axis of the cylindrical body; as well as The second discharge valve is configured to block the second discharge path and is lifted by the refrigerant compressed by the rotation of the rotating body, causing the refrigerant to be discharged. For each of the aforementioned cylindrical bodies, at least one of the more than one first ejection path and at least one of the more than one second ejection path are offset by a certain distance in the direction perpendicular to the axial direction. 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 covering component, a first cylinder as the cylindrical body, and a partition plate as the second covering component. The second compression mechanism includes a second bearing as the first cover member, a second cylinder as the cylindrical body, and a partition plate as the second cover member. The partition plate has a first flow path and a second flow path for the refrigerant discharged from the first discharge valve and the second discharge valve. The first flow path and the second flow path are configured such that they do not overlap in the axial direction with the spaces that are continuous with each suction path in two spaces formed in the first cylinder and the second cylinder, respectively.

6. A heat exchange system, characterized in that, It includes the compressor according to any one of claims 1 to 5, and the refrigerant is circulated through the compressor for heat exchange.

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