CN202900660U - Dual-rotor two-stage enthalpy-increasing compressor, air conditioner and heat pump water heater - Google Patents

Abstract

The utility model discloses a birotor two-stage enthalpy-increasing compressor, air conditioner and heat pump water heater, birotor two-stage enthalpy-increasing compressor, including casing, bent axle, upper flange, high pressure cylinder, baffle, low pressure cylinder, lower flange, lower cover plate and enthalpy-increasing pipe, the upper flange has first exhaust port, the high pressure cylinder has high pressure induction port and high pressure gas vent, the low pressure cylinder has low pressure induction port and low pressure gas vent, the lower flange has the second gas vent; the maximum distance a between the low pressure exhaust port edge and the axis of the crankshaft is greater than the maximum distance b between the high pressure exhaust port edge and the axis of the crankshaft. The utility model provides a birotor two-stage enthalpy-increasing compressor can reduce the suction and exhaust resistance in high, low pressure compression chamber to reduce the clearance volume of high pressure jar, improve the volume efficiency, thereby improve the holistic performance of compressor.

Description

Dual-rotor two-stage enthalpy-increasing compressor, air conditioner and heat pump water heater

technical field

The utility model relates to a compressor, in particular to a double-rotor, two-stage enthalpy-increasing compressor, and an air conditioner and a heat pump water heater using the double-rotor, two-stage enthalpy-increasing compressor.

Background technique

The pump body assembly of the dual-rotor two-stage enthalpy-increasing compressor in the prior art includes a crankshaft, an upper flange, a high-pressure cylinder, a partition, a low-pressure cylinder, a lower flange, and a lower cover plate. The upper flange has an exhaust port, and the high-pressure The cylinder has a high-pressure suction port and a high-pressure exhaust port, the low-pressure cylinder has a low-pressure suction port and a low-pressure exhaust port, and the lower flange has an exhaust port. The maximum distance between the edge of the low-pressure exhaust port of the low-pressure cylinder of the prior art dual-rotor two-stage enthalpy-increasing compressor and the axis of the crankshaft is equal to the maximum distance between the edge of the high-pressure exhaust port of the high-pressure cylinder and the axis of the crankshaft. As a result, the suction and exhaust resistance of the high and low compression chambers is relatively large, and the clearance volume of the high-pressure cylinder is large and the working volume is reduced, so that the overall energy efficiency of the compressor is low.

Contents of the invention

Aiming at the current state of the art above, the technical problem to be solved by this utility model is to provide a dual-rotor two-stage enthalpy-increasing compressor with low suction and exhaust resistance in the high and low compression chambers and a large clearance volume in the high-pressure cylinder , to increase the volumetric efficiency, thereby improving the overall performance of the compressor.

Another technical problem to be solved by the utility model is to provide an air conditioner with the above-mentioned dual-rotor two-stage enthalpy-increasing compressor.

Another technical problem to be solved by the utility model is to provide a heat pump water heater with the above-mentioned dual-rotor two-stage enthalpy-increasing compressor.

The technical scheme adopted by the utility model to solve the above-mentioned technical problems is: a double-rotor two-stage enthalpy-increasing compressor, including a shell, a crankshaft, an upper flange, a high-pressure cylinder, a partition, a low-pressure cylinder, a lower flange, and a lower cover plate and enthalpy increasing pipe, the upper flange has a first exhaust port, the high-pressure cylinder has a high-pressure suction port and a high-pressure exhaust port, the low-pressure cylinder has a low-pressure suction port and a low-pressure exhaust port, the The lower flange has a second exhaust port; the maximum distance a between the edge of the low-pressure exhaust port and the axis of the crankshaft is greater than the distance a between the edge of the high-pressure exhaust port and the axis of the crankshaft The maximum distance b.

In one of the embodiments, the maximum distance c between the edge of the second exhaust port and the axis of the crankshaft is greater than the maximum distance c between the edge of the first exhaust port and the axis of the crankshaft. distance d.

In one of the embodiments, it further includes a medium-pressure chamber, and the medium-pressure chamber communicates with the low-pressure exhaust port, the high-pressure suction port and the enthalpy-increasing pipe.

In one of the embodiments, the lower flange is provided with a first inner chamber, and the opening of the first inner chamber is sealed by the lower cover plate to form the medium-pressure chamber.

In one of the embodiments, an intermediate cylinder is provided between the partition plate and the low-pressure cylinder, and a second inner chamber is provided on the intermediate cylinder, and the opening of the second inner chamber is formed by sealing the partition board. Described medium pressure chamber.

In one of the embodiments, an intermediate cylinder is provided outside the housing, and the intermediate pressure chamber is provided on the intermediate cylinder.

The technical solution adopted by the utility model to solve the above-mentioned technical problems is: an air conditioner, including a compressor, and the compressor is the above-mentioned double-rotor two-stage enthalpy-increasing compressor.

The technical solution adopted by the utility model to solve the above-mentioned technical problems is: a heat pump water heater, including a compressor, and the compressor is the above-mentioned double-rotor two-stage enthalpy-increasing compressor.

Tests have shown that under the same cooling capacity, the dual-rotor two-stage enthalpy-increasing compressor provided by the utility model can reduce the suction and exhaust resistance of the high and low pressure compression chambers, reduce the clearance volume of the high pressure cylinder, and improve the volumetric efficiency , thereby improving the overall performance of the compressor.

Description of drawings

Fig. 1 is a schematic structural diagram of a dual-rotor two-stage enthalpy-increasing compressor in Embodiment 1 of the utility model, and the direction indicated by the arrow in the figure is the flow direction of the refrigerant;

Fig. 2 is a schematic cross-sectional structural view of the pump body assembly of the dual-rotor two-stage enthalpy-increasing compressor described in Fig. 1;

Fig. 3 is a front structural schematic diagram of the low-pressure cylinder of the dual-rotor two-stage enthalpy-increasing compressor described in Fig. 1;

Fig. 4 is a front structural schematic diagram of the high-pressure cylinder of the dual-rotor two-stage enthalpy-increasing compressor described in Fig. 1;

Fig. 5 is a front structural schematic diagram of the lower flange of the dual-rotor two-stage enthalpy-increasing compressor described in Fig. 1;

Fig. 6 is a front structural schematic view of the upper flange of the dual-rotor two-stage enthalpy-increasing compressor described in Fig. 1;

Fig. 7 is a schematic structural diagram of a dual-rotor two-stage enthalpy-increasing compressor in Embodiment 2 of the present utility model;

Fig. 8 is a structural schematic diagram of the dual-rotor two-stage enthalpy-increasing compressor in Embodiment 3 of the present utility model;

Figure 9 is a graph showing the relationship between the suction and exhaust resistance of the low-pressure cylinder as a function of a/b;

Figure 10 is a graph showing the relationship between the suction and exhaust resistance of the high-pressure cylinder as a function of a/b;

Fig. 11 is a curve diagram of the relationship between the volumetric efficiency of the high-pressure cylinder and the change of b/a;

Fig. 12 is a curve diagram of energy efficiency ratio changing with b/a;

Figure 13 is a graph showing the relationship between energy efficiency ratio and d/c.

In the above figures, 1-liquid distributor; 2-low pressure cylinder; 2a-low pressure suction port; 2b-low pressure exhaust port; 3-lower flange; 3a-second exhaust port; 3b-first inner cavity ;4-lower cover plate;5-enthalpy increasing sealing ring;6-enthalpy increasing pump body suction pipe;7-enthalpy increasing shell suction pipe;8-enthalpy increasing pipe;9-crankshaft;10-low pressure roller; 11-partition; 12-high pressure cylinder; 12a-high pressure suction port; 12b-high pressure exhaust port; 13-high pressure roller; 14-upper flange; 14a-first exhaust port; 15-motor stator; 16 - motor rotor; 17 - housing; 18 - upper cover assembly; 19 - exhaust pipe; 20 - middle cylinder; 20a - second inner cavity.

Detailed ways

The utility model is described in detail below with reference to the accompanying drawings and in conjunction with the embodiments. It should be noted that, in the case of no conflict, the following embodiments and features in the embodiments can be combined with each other.

Embodiment one

As shown in Figure 1, the dual-rotor two-stage enthalpy-increasing compressor in this embodiment includes a casing 17, a pump body assembly arranged at the lower part of the inner cavity of the casing 17, a motor arranged above the pump body assembly, and a The upper cover assembly 18 on the top of 17, the liquid distributor 1 welded and fixed on the housing 17, and the enthalpy increasing structural assembly, the motor includes a motor rotor 16 and a motor stator 15. The enthalpy-increasing structural assembly includes an enthalpy-increasing pipe 8 , an enthalpy-increasing sealing ring 5 , an enthalpy-increasing pump body suction pipe 6 and an enthalpy-increasing housing suction pipe 7 , and the upper cover assembly 18 includes an exhaust pipe 19 .

Figure 2 is a schematic structural diagram of the pump body assembly, the pump body assembly includes a crankshaft 9, an upper flange 14, a high-pressure cylinder 12, a high-pressure roller 13, a high-pressure slide, a partition 11, a low-pressure cylinder 2, a low-pressure roller 10, The low-pressure sliding vane, the lower flange 3 and the lower cover plate 4, wherein the upper flange 14 and the lower flange 3 are used to support the crankshaft 9, the low-pressure cylinder 2, the low-pressure roller 10 and the low-pressure sliding vane together form a low-pressure compression chamber, and the high-pressure The cylinder 12, the high-pressure roller 13 and the high-pressure slide jointly form a high-pressure compression chamber, and the partition plate 11 is used to separate the high-pressure compression chamber and the low-pressure compression chamber.

Figure 3 is a schematic diagram of the front view of the low-pressure cylinder 2. The low-pressure cylinder 2 has a low-pressure chamber, a low-pressure suction port 2a connected to the low-pressure chamber, and a low-pressure exhaust port 2b. The low-pressure suction port 2a is connected to the liquid separator through the suction pipe 1, the low-pressure exhaust port 2b communicates with the inner cavity of the lower flange 3, and the maximum distance between the edge of the low-pressure exhaust port 2b and the axis of the crankshaft 9 is a.

Fig. 4 shows the schematic diagram of the front structure of the high-pressure cylinder 12. The low-pressure cylinder 2 has a high-pressure chamber, a high-pressure suction port 12a communicated with the low-pressure chamber, and a high-pressure exhaust port 12b. An inner cavity 3b is connected, and the maximum distance between the edge of the high-pressure exhaust port 12b and the axis of the crankshaft 9 is b, and a is greater than b. Figure 9 is a diagram showing the relationship between the suction and exhaust resistance of the low-pressure cylinder as a function of a/b, and Figure 10 is a diagram of the relationship between the suction and exhaust resistance of the high-pressure cylinder as a function of a/b. Under certain circumstances, the dual-rotor two-stage enthalpy-increasing compressor of the embodiment of the utility model can reduce the suction and exhaust resistance of the high and low pressure compression chambers. Fig. 11 is a curve diagram of the relationship between the volumetric efficiency of the high-pressure cylinder and b/a, and Fig. 12 is a curve diagram of the relationship between the energy efficiency ratio and the variation of b/a. It can be seen from Figs. The enthalpy-increasing compressor can reduce the clearance volume of the high-pressure cylinder 12, increase the volumetric efficiency, and thereby improve the overall performance of the compressor.

FIG. 5 is a schematic front view of the lower flange 3 , the lower flange 3 has a second exhaust port 3 a, and the maximum distance c between the edge of the second exhaust port 3 a and the axis of the crankshaft 9 . The lower flange 3 is provided with a first inner chamber 3b and an enthalpy-increasing port communicating with the first inner chamber 3b. The opening of the first inner chamber 3b is sealed by the lower cover plate 4 to form a medium-pressure chamber. The low-pressure exhaust port 2b, the high-pressure suction port 12a and the enthalpy increasing pipe 8 are connected.

FIG. 6 is a schematic front view of the upper flange 14. The upper flange 14 has a first exhaust port 14a, and the distance between the edge of the first exhaust port 14a and the axis of the crankshaft 9 is The maximum distance is d, and c is greater than d. Figure 13 is a graph showing the relationship between energy efficiency ratio and d/c. It can be seen from Figure 13 that since c is greater than d, the overall performance of the compressor can be further improved under the same cooling capacity.

The refrigerant circulation process of the compressor of the present embodiment is briefly described below in conjunction with FIG. 1:

Driven by the motor, the compressor runs, and the refrigerant coming back from the system enters the low-pressure cylinder 2 through the liquid separator 1 and is compressed and discharged to the lower flange 3. The other part of the refrigerant comes from another circuit of the system to increase enthalpy. Pipe 8, then enters the suction pipe 6 of the enthalpy-increasing pump body, flows into the lower flange 3 through the enthalpy-increasing port on the low-pressure cylinder 2, and mixes with the refrigerant coming in from the compressor of the low-pressure cylinder 2 to form a medium-pressure mixed refrigerant fluid , the fluid passes through the flow groove on the low-pressure cylinder 2 and flows through the partition 11, is sucked by the high-pressure cylinder 12 and compressed into a high-pressure refrigerant fluid, and is discharged through the upper flange 14 to the space surrounded by the housing 17 and the upper cover assembly 18 Inside, and discharged to the system (evaporator or condenser) from the exhaust pipe 19, that is to complete a two-stage compression of the compressor and the working process of increasing enthalpy.

Embodiment two

As shown in Figure 7, the structure of the dual-rotor, two-stage enthalpy-increasing compressor in this embodiment is substantially the same as that of the dual-rotor, two-stage enthalpy-increasing compressor in Embodiment 1, except that: 11 and the low-pressure cylinder 2 are provided with an intermediate cylinder 20, the intermediate cylinder 20 is fixed on the low-pressure cylinder 2 by screws, the intermediate cylinder 20 is provided with a second inner cavity 20a, and the opening of the second inner cavity 20a is formed by The partition plate 11 is sealed to form a medium-pressure chamber, which communicates with the low-pressure exhaust port 2 b, the high-pressure suction port 12 a and the enthalpy increasing pipe 8 .

The refrigerant circulation process of the compressor of the present embodiment is as follows:

The refrigerant gas flows from the air conditioning system through the separator into the low-pressure suction port 2a on the low-pressure cylinder 2, the refrigerant gas compressed by the low-pressure cylinder 2 flows into the intermediate cylinder 20, and the other part of the refrigerant gas flows through the enthalpy increasing pipe 8 and then passes through the intermediate cylinder 20 The suction port on the top also flows into the middle cylinder 20 and mixes with the gas flowing in from the previous part, then flows into the suction side of the high-pressure cylinder 12 through the flow hole on the partition plate 11, and then passes through the suction side of the upper flange 14 after being compressed by the high-pressure cylinder 12. The first exhaust port 14a is discharged out of the pump body, and finally flows into the air-conditioning system through the compressor exhaust pipe 19, and flows back to the compressor after being evaporated by the air-conditioning system to complete a cycle.

Embodiment three

As shown in Figure 8, the structure of the dual-rotor, two-stage enthalpy-increasing compressor in this embodiment is substantially the same as that of the dual-rotor, two-stage enthalpy-increasing compressor in Embodiment 1, except that: 17. An intermediate cylinder 20 is welded and fixed on the outside, and a medium-pressure cavity is arranged on the intermediate cylinder 20. The medium-pressure cavity communicates with the low-pressure exhaust port 2b, the high-pressure suction port 12a and the enthalpy-increasing pipe 8. The circulation process of the refrigerant in the compressor of this embodiment is the same as that of the second embodiment, and will not be repeated here.

The above-mentioned embodiments only express several implementations of the utility model, and the description thereof is relatively specific and detailed, but it should not be construed as limiting the patent scope of the utility model. It should be noted that those skilled in the art can make several modifications and improvements without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the scope of protection of the utility model patent should be based on the appended claims.

Claims (8)

1. A dual-rotor two-stage enthalpy-increasing compressor, comprising a housing, a crankshaft, an upper flange, a high-pressure cylinder, a dividing plate, a low-pressure cylinder, a lower flange and an enthalpy-increasing pipe, and the upper flange has a first exhaust port, the high-pressure cylinder has a high-pressure suction port and a high-pressure exhaust port, the low-pressure cylinder has a low-pressure suction port and a low-pressure exhaust port, and the lower flange has a second exhaust port; it is characterized in that the The maximum distance a between the edge of the low-pressure exhaust port and the axis of the crankshaft is greater than the maximum distance b between the edge of the high-pressure exhaust port and the axis of the crankshaft. 2. The dual-rotor two-stage enthalpy-increasing compressor according to claim 1, characterized in that the maximum distance c between the edge of the second exhaust port and the axis of the crankshaft is greater than that of the first row The maximum distance d between the port edge and the axis of the crankshaft. 3. The dual-rotor two-stage enthalpy-increasing compressor according to claim 1 or 2, characterized in that it also includes a medium-pressure chamber, which is connected to the low-pressure exhaust port, the high-pressure suction port and the The enthalpy-increasing tubes are connected. 4. The dual-rotor two-stage enthalpy-increasing compressor according to claim 3, characterized in that, the lower flange is provided with a first inner cavity, and the opening of the first inner cavity is sealed by the lower cover to form the Medium pressure cavity. 5. The dual-rotor two-stage enthalpy-increasing compressor according to claim 3, characterized in that, an intermediate cylinder is provided between the partition plate and the low-pressure cylinder, and a second inner cavity is provided on the intermediate cylinder, The opening of the second inner chamber is sealed by the partition to form the medium-pressure chamber. 6 . The dual-rotor two-stage enthalpy-increasing compressor according to claim 3 , characterized in that, an intermediate cylinder is arranged outside the housing, and the intermediate pressure chamber is arranged on the intermediate cylinder. 7 . 7. An air conditioner, comprising a compressor, characterized in that the compressor is a dual-rotor, two-stage enthalpy-increasing compressor according to any one of claims 1-6. 8. A heat pump water heater, comprising a compressor, characterized in that the compressor is a dual-rotor, two-stage enthalpy-increasing compressor according to any one of claims 1-6.

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