CN204141904U - Refrigerant flow direction converting - Google Patents
Refrigerant flow direction converting Download PDFInfo
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- CN204141904U CN204141904U CN201420437932.8U CN201420437932U CN204141904U CN 204141904 U CN204141904 U CN 204141904U CN 201420437932 U CN201420437932 U CN 201420437932U CN 204141904 U CN204141904 U CN 204141904U
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Abstract
The utility model discloses a kind of refrigerant flow direction converting, it comprises high pressure compressor, low pressure compressor, the first check valve, the second check valve, the first cross valve; The low pressure node of the first cross valve is connected with the second tie point of refrigerant flow direction converting by the 61 pipeline, the high voltage nodes of the first cross valve is connected with the 61 pipeline through the port of export of low pressure compressor, the arrival end of low pressure compressor successively, and the first tie point of refrigerant flow direction converting is connected with the 61 pipeline through the arrival end of the port of export of the 63 pipeline, high pressure compressor, high pressure compressor, the 64 pipeline, the second one-way valved outlet end, the second one-way valve inlet end successively.Make heat-pump apparatus, or the compressor bank in heat pump type air conditioner refrigeration plant can realize freely switching of single/double stage compression as required.
Description
Technical field
The utility model relates to a kind of refrigerant flow direction converting, belongs to technical field of air conditioner refrigeration.
background technology
In recent years, along with the raising of expanding economy and people's living standard, the operation of air conditioning systems of Teat pump boiler and pump type heat obtains large-scale application in industry and civil area, technical merit has had large increase, but still have much room for improvement in many embody rule, such as: for air source hot pump water heater, it for the whole year for user produces hot water, when summer operation, because outside air temperature is higher, compressor single stage compress runs hot water and the water yield that just can produce water temperature required for user, and maintains higher service behaviour; And when running in the winter time, because outside air temperature is lower, time particularly lower than-5 DEG C, compressor single stage compress is run and is just difficult to hot water and the water yield of producing water temperature required for user, and ensure normal operation and maintain comparatively high workload performance; Now compressor just needs to adopt Two-stage Compression to run, that is: for air source hot pump water heater, its compressor or compressor bank should be able to change according to the height of outside air temperature, can realize single stage compress run or Two-stage Compression run freely switch; The patent of invention that present invention applicant obtained the authorization on 07 25th, 2012, right number is 201010267689.6 just proposed this kind of scheme, as shown in the utility model Fig. 5.In the course of the work, when magnetic valve 46 cuts out, low pressure compressor 1-1, high pressure compressor 1-2 are in parallel connection to the program, and any one in two compressors is run, or when two compressors run simultaneously, compressor is all in single stage compress running status; In the course of work, when magnetic valve 46 is opened, and low pressure compressor 1-1, high pressure compressor 1-2 all in running order time, low pressure compressor 1-1, high pressure compressor 1-2 are in series connection, low pressure compressor 1-1, high pressure compressor 1-2 form the Two-stage Compression running status of compressing mechanism 1 jointly, therefore still can maintain normal operation under lower outside air temperature, and keep higher service behaviour; But it must be noted that: such scheme, when applying, exists following defect:
1) magnetic valve 46 coil is comparatively large, the serious easily initiating failure of heating, and cost is higher;
2) when magnetic valve 46 cuts out, low pressure compressor 1-1, high pressure compressor 1-2 is in parallel connection, and high pressure compressor 1-2 normally runs, and low pressure compressor 1-1 is not when running, in the long course of work, due to the minor leakage of the 5th check valve 25, unavoidably progressively can set up an elevated pressures at the low pressure compressor 1-1 port of export, and now low pressure compressor 1-1 arrival end is in a lower high pressure compressor 1-2 pressure of inspiration(Pi), therefore larger pressure differential can be there is between the low pressure compressor 1-1 port of export and arrival end, so when low pressure compressor 1-1 also needs to drop into parallel operation, the starting current of its compressor electric motor will be larger, easily cause the damage of low pressure compressor 1-1 motor.
The utility model right that the hvac equipment Co., Ltd of Guangdong U.S. obtained the authorization on 06 11st, 2014, right number is 201320719147.7 it is also proposed similar scheme, as shown in Fig. 6, Fig. 7 of the present invention.As shown in Figure 6, Figure 7, in the course of work, switched by the flow direction of cross valve 3, make the first compressor bank 1 and the second compressor bank 2 realize being connected in parallel and being connected in series, thus make the first compressor bank 1 and the second compressor bank 2 form single stage compress in parallel to run and Two-stage Compression of connecting runs, as can be seen from Figure 7: when the first compressor bank 1 and the second compressor bank 2 form single stage compress in parallel run time, first working hole of cross valve 3 and the inlet communication of cross valve 3, second working hole of cross valve 3 and the outlet of cross valve 3, therefore, when the second compressor bank 2 works, and the first compressor bank 1 is not when working, also there is the defect that shown in the utility model Fig. 5, scheme is same, that is: in the long course of work, due to the minor leakage of check valve 5, unavoidably progressively can set up an elevated pressures in the gas outlet of the first compressor bank 1, and now the first compressor bank 1 air inlet is in lower main muffler 7 pressure, therefore a larger pressure differential can be there is between the first compressor bank 1 gas outlet and air inlet, so when the first compressor bank 1 also needs to drop into parallel operation, the starting current of its compressor electric motor will be larger, easily cause the damage of the first compressor bank 1 motor.
In addition, as shown in Figure 7, when the first compressor bank 1 and the second compressor bank 2 form single stage compress in parallel run time, the low pressure refrigerant vapor entering the second compressor bank 2 air inlet from main muffler 7 must first through intercooler 401, because under this operating mode, intercooler 401 does not work usually, therefore due to the existence of intercooler 401, adds the inspiratory resistance of the second compressor bank 2 undoubtedly.
summary of the invention
The purpose of this utility model be to provide a kind of structure simple, reliably, can heat-pump apparatus be made, or the compressor in heat pump type air conditioner refrigeration plant realizes single/double stage and compresses the refrigerant flow direction converting freely switched; And this refrigerant flow direction converting is in single stage compress situation, high pressure compressor works, and low pressure compressor is not when working, the port of export of low pressure compressor and the pressure of arrival end can be made to be consistent, when making low pressure compressor also need to drop into parallel operation, the starting current of its compressor electric motor is less.
In order to overcome above-mentioned technology Problems existing, the technical scheme of the utility model technical solution problem is:
A kind of refrigerant flow direction converting, comprises high pressure compressor (1), low pressure compressor (2), the first check valve (21), the second check valve (22); It is characterized in that: this refrigerant flow direction converting also comprises the first cross valve (70);
The low pressure node (73) of described first cross valve (70) is connected with second tie point (102) of refrigerant flow direction converting by the 61 pipeline (61), the high voltage nodes (71) of described first cross valve (70) is successively through the port of export of described low pressure compressor (2), the arrival end of low pressure compressor (2) is connected with the 61 pipeline (61), first tie point (101) of refrigerant flow direction converting is successively through the 63 pipeline (63), the port of export of described high pressure compressor (1), the arrival end of high pressure compressor (1), 64 pipeline (64), described second check valve (22) port of export, second check valve (22) arrival end is connected with the 61 pipeline (61), any one node (72) in described first cross valve (70) two commutation node is successively through described first check valve (21) arrival end, first check valve (21) port of export, 62 pipeline (62) is connected with the 63 pipeline (63), another commutation node (74) of described first cross valve (70) is connected by the 64 pipeline (64) between the arrival end of the 65 pipeline (65) and described high pressure compressor (1) and the second check valve (22) port of export.
Compared with prior art, its beneficial effect is the utility model:
1. make heat-pump apparatus, or the compressor in heat pump type air conditioner refrigeration plant can realize freely switching of single/double stage compression as required;
2. in single stage compress situation, high pressure compressor works, and when low pressure compressor does not work, the port of export of low pressure compressor and the pressure of arrival end can be made to be consistent, therefore, when low pressure compressor also needs to drop into parallel operation, the starting current of its motor can be made less;
3. structure is simple, and reliable operation is with low cost;
4. the utility model is specially adapted to the heat-pump apparatus that in industry and civil area, low-temperature heat source temperature changes greatly, or heat pump type air conditioner refrigeration plant.
accompanying drawing explanation
Fig. 1 is the utility model embodiment 1 structural representation;
Fig. 2 is the utility model embodiment 2 structural representation;
Fig. 3 is the utility model embodiment 3 structural representation;
Fig. 4 is the utility model embodiment 4 structural representation;
Fig. 5 is prior art structural representation;
Fig. 6 is prior art structural representation;
Fig. 7 is prior art structural representation.
detailed description of the invention
Below in conjunction with accompanying drawing, the utility model content is described in further detail.
Embodiment 1
Be heat-pump apparatus shown in Fig. 1, be applicable to industry and civil area has the occasion of heat demand.
Heat-pump apparatus shown in Fig. 1 comprises following part: refrigerant flow direction converting 100, First Heat Exchanger 3, second heat exchanger 4, first throttle mechanism 5, second throttle body 6, liquid reservoir 7.
First Heat Exchanger 3 is cold-producing medium-water-to-water heat exchangers, during work, as condenser, for the production of domestic hot-water;
Second heat exchanger 4 is also a cold-producing medium-water-to-water heat exchanger, during work, as evaporimeter, and the low-temperature heat source place draw heat outdoor in environment;
First throttle mechanism 5, second throttle body 6 are electric expansion valve;
Refrigerant flow direction converting 100 comprises following a few part: low pressure compressor 2, high pressure compressor 1, first cross valve 70, first check valve 21, second check valve 22.
The annexation of each parts of refrigerant flow direction converting 100 is as follows: the low pressure node 73 of the first cross valve 70 is connected with the second tie point 102 of refrigerant flow direction converting 100 by the 61 pipeline 61, the high voltage nodes 71 of the first cross valve 70 is successively through the port of export of low pressure compressor 2, the arrival end of low pressure compressor 2 is connected with the 61 pipeline 61, first tie point 101 of refrigerant flow direction converting 100 is successively through the 63 pipeline 63, the port of export of high pressure compressor 1, the arrival end of high pressure compressor 1, 64 pipeline 64, second check valve 22 port of export, second check valve 22 arrival end is connected with the 61 pipeline 61, any one node 72 in first cross valve 70 2 commutation node is successively through the first check valve 21 arrival end, first check valve 21 port of export, 62 pipeline 62 is connected with the 63 pipeline 63, another commutation node 74 of first cross valve 70 is connected by the 64 pipeline 64 between the arrival end of the 65 pipeline 65 and high pressure compressor 1 and second check valve 22 port of export.
The annexation of each part of the heat-pump apparatus shown in Fig. 1 is as follows:
First tie point 101 of refrigerant flow direction converting 100 is successively through First Heat Exchanger 3, 41 pipeline 41, liquid reservoir 7, 42 pipeline 42, first throttle mechanism 5, 43 pipeline 43, second heat exchanger 4, 44 pipeline 44 is connected with the second tie point 102 of refrigerant flow direction converting 100, second throttle body 6 one end is connected with liquid reservoir 7 by the 45 pipeline 45, second throttle body 6 other end passes through the 64 pipeline 64 between the arrival end of blowdown pipe 46 and high pressure compressor 1 and second check valve 22 port of export, or the 65 pipeline 65 be connected.
In the course of work, the heat-pump apparatus shown in Fig. 1 can realize single stage compress operating condition and Two-stage Compression operating condition, and the workflow under each operating mode is as described below.
(1) single stage compress operating condition
Under this operating mode, high pressure compressor 1, low pressure compressor 2 are in parallel connection.During work, there is following operating scheme.
1) high pressure compressor 1, low pressure compressor 2 work simultaneously
Now, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70.First throttle mechanism 5 normally works, and second throttle body 6 is closed.Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 1 is as described below:
From the second heat exchanger 4 low-temperature low-pressure refrigerant gas out successively through the second tie point 102 of the 44 pipeline 44, refrigerant flow direction converting 100, enter the 61 pipeline 61 and be divided into two-way; The first via, successively through the second check valve 22 arrival end, second check valve 22 port of export, the 64 pipeline 64, enters after high pressure compressor 1 compressed, then is discharged into the 63 pipeline 63; Second tunnel enters after low pressure compressor 2 compressed, again successively through commutation node 72, first check valve 21 arrival end, first check valve 21 port of export, the 62 pipeline 62 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, be also discharged into the 63 pipeline 63; Two-way gas is after the 63 pipeline 63 mixes, again successively through the first tie point 101, First Heat Exchanger the 3, the 41 pipeline 41, liquid reservoir the 7, the 42 pipeline 42, first throttle mechanism the 5, the 43 pipeline 43 of refrigerant flow direction converting 100, get back to again the second heat exchanger 4, so far complete the heat pump cycle of the single stage compress that once two compressors run simultaneously.
2) high pressure compressor 1 works, and low pressure compressor 2 does not work
Now, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70.First throttle mechanism 5 normally works, and second throttle body 6 is closed.Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 1 is as described below:
From the second heat exchanger 4 low-temperature low-pressure refrigerant gas out successively through the 44 pipeline 44, second tie point 102 of refrigerant flow direction converting 100, 61 pipeline 61, second check valve 22 arrival end, second check valve 22 port of export, 64 pipeline 64, enter after high pressure compressor 1 compressed, again successively through the 63 pipeline 63, first tie point 101 of refrigerant flow direction converting 100, First Heat Exchanger 3, 41 pipeline 41, liquid reservoir 7, 42 pipeline 42, first throttle mechanism 5, 43 pipeline 43, get back to again the second heat exchanger 4, so far the heat pump cycle of the single stage compress of a high pressure compressor 1 isolated operation is completed.
When working under this scenario, the port of export of low pressure compressor 2 and the refrigerant pressure of arrival end are consistent, under being all in the pressure of inspiration(Pi) of high pressure compressor 1.
(2) Two-stage Compression operating condition
Under this operating mode, high pressure compressor 1, low pressure compressor 2 all work, and are in series connection.During work, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70.
First throttle mechanism 5, second throttle body 6 all normally work, and first throttle mechanism 5, for the throttling of refrigerant liquid, controls the refrigerant flow by the second heat exchanger 4; Second throttle body 6 for controlling the air compensation in Two-stage Compression process, thus controls the delivery temperature of intermediate pressure or high pressure compressor 1; Usually when second throttle body 6 be connected with the fluid space of liquid reservoir 7 time, be controlled by the delivery temperature of mode to the intermediate pressure in Two-stage Compression process or high pressure compressor 1 of hydrojet; When second throttle body 6 be connected with the gas compartment of liquid reservoir 7 time, be controlled by the delivery temperature of jet mode to the intermediate pressure in Two-stage Compression process or high pressure compressor 1.
Under this operating condition, the workflow of heat-pump apparatus shown in Fig. 1 is as described below:
From First Heat Exchanger 3 refrigerant liquid out, enter liquid reservoir 7 through the 41 pipeline 41, be divided into two-way; First via cold-producing medium is successively through the second tie point the 102, the 61 pipeline 61 of the 42 pipeline 42, first throttle mechanism the 5, the 43 pipeline 43, second heat exchanger the 4, the 44 pipeline 44, refrigerant flow direction converting 100, enter after low pressure compressor 2 compressed by the first order, again successively through commutation node the 74, the 65 pipeline 65 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, enter the 64 pipeline 64; Second road cold-producing medium, successively through the 45 pipeline 45, second throttle body 6, blowdown pipe 46, also enters the 64 pipeline 64; Two-way cold-producing medium is after the 64 pipeline 64 mixes, enter high pressure compressor 1 again to be compressed by the second level, and then successively through the first tie point 101 of the 63 pipeline 63, refrigerant flow direction converting 100, get back to again First Heat Exchanger 3, so far complete the two-stage compression heat pump circulation of a sub-band second vapor injection.
Embodiment 2
As shown in Figure 2, the difference of heat-pump apparatus shown in it and embodiment 1 Fig. 1 is: in the heat-pump apparatus shown in the present embodiment Fig. 2, adds the 3rd check valve 23; 3rd check valve 23 connected mode is in systems in which: the arrival end of the 3rd check valve 23 is connected with the port of export of high pressure compressor 1, and the port of export of the 3rd check valve 23 is connected with the 62 pipeline 62 with the 63 pipeline 63.
In the course of work, heat-pump apparatus shown in the present embodiment Fig. 2 is except realizing all operating conditions of heat-pump apparatus shown in the utility model embodiment 1 Fig. 1, and beyond all operating schemes under all operating conditions, following operating scheme can also be realized for single stage compress operating condition, that is: high pressure compressor 1 does not work, the operating scheme that low pressure compressor 2 works.
Under this operating scheme, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70.First throttle mechanism 5 normally works, and second throttle body 6 is closed.Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 2 is as described below:
From the second heat exchanger 4 low-temperature low-pressure refrigerant gas out successively through the 44 pipeline 44, second tie point 102 of refrigerant flow direction converting 100, 61 pipeline 61, enter after low pressure compressor 2 compressed, again successively through the high voltage nodes 71 of the first cross valve 70, the commutation node 72 of the first cross valve 70, first check valve 21 arrival end, first check valve 21 port of export, 62 pipeline 62, 63 pipeline 63, first tie point 101 of refrigerant flow direction converting 100, First Heat Exchanger 3, 41 pipeline 41, liquid reservoir 7, 42 pipeline 42, first throttle mechanism 5, 43 pipeline 43, get back to again the second heat exchanger 4, so far the heat pump cycle of the single stage compress of a low pressure compressor 2 isolated operation is completed.
Embodiment 3
As shown in Figure 3, the difference of heat-pump apparatus shown in it and the utility model embodiment 1 Fig. 1 is: in the heat-pump apparatus shown in the present embodiment Fig. 3, adds second cross valve 80 and the 3rd throttle mechanism 9.
Second cross valve 80 with the 3rd throttle mechanism 9 connected mode is in systems in which: the high voltage nodes 81 of the second cross valve 80 is connected with the first tie point 101 of refrigerant flow direction converting 100, the low pressure node 83 of the second cross valve 80 is connected with the second tie point 102 of refrigerant flow direction converting 100, any one commutation node 82 in second cross valve 80 two commutation node is successively by First Heat Exchanger 3, 41 pipeline 41, 3rd throttle mechanism 9, liquid reservoir 7, 42 pipeline 42, first throttle mechanism 5, 43 pipeline 43, second heat exchanger 4, 44 pipeline 44 is connected with another node 84 that commutates of the second cross valve 80.
During work, First Heat Exchanger 3, second heat exchanger 4 in the heat-pump apparatus shown in the present embodiment Fig. 3 can play the part of the dual role of condenser and evaporimeter respectively; When First Heat Exchanger 3 is condensers, for the production of hot water, and the second heat exchanger 4 is evaporimeters, during for absorbing heat from low-temperature heat source, heat-pump apparatus shown in the present embodiment Fig. 3 can realize all operating conditions of heat-pump apparatus shown in the utility model embodiment 1 Fig. 1, and all operating schemes under all operating conditions, realize the heat supply to user; When the First Heat Exchanger 3 in the heat-pump apparatus shown in Fig. 3 is evaporimeters, for the production of chilled water, and the second heat exchanger 4 is condensers, and during for discharging condensation heat in environment, the heat-pump apparatus shown in the present embodiment Fig. 3 can realize the cooling to user.
The workflow of heat-pump apparatus shown in Fig. 3 under each operating condition is as described below.
(1) single stage compress operating condition (First Heat Exchanger 3 is to user's heat supply)
Under this operating mode, high pressure compressor 1, low pressure compressor 2 are in parallel connection.During work, there is following operating scheme.
1) high pressure compressor 1, low pressure compressor 2 work simultaneously
Now, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70;
The high voltage nodes 81 of the second cross valve 80 communicates with the commutation node 82 of the second cross valve 80, and the low pressure node 83 of the second cross valve 80 communicates with the commutation node 84 of the second cross valve 80.
First throttle mechanism 5 normally works, and second throttle body 6 is closed, the 3rd throttle mechanism 9 standard-sized sheet.
Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 3 is as described below:
From the second heat exchanger 4 low-temperature low-pressure refrigerant gas out successively through the low pressure node 83 of commutation node 84, second cross valve 80, second tie point 102 of refrigerant flow direction converting 100 of the 44 pipeline 44, second cross valve 80, enter the 61 pipeline 61 and be divided into two-way; The first via, successively through the second check valve 22 arrival end, second check valve 22 port of export, the 64 pipeline 64, enters after high pressure compressor 1 compressed, then is discharged into the 63 pipeline 63; Second tunnel enters after low pressure compressor 2 compressed, again successively through commutation node 72, first check valve 21 arrival end, first check valve 21 port of export, the 62 pipeline 62 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, be also discharged into the 63 pipeline 63; Two-way gas is after the 63 pipeline 63 mixes, again successively through commutation node 82, First Heat Exchanger the 3, the 41 pipeline 41, the 3rd throttle mechanism 9, liquid reservoir the 7, the 42 pipeline 42, first throttle mechanism the 5, the 43 pipeline 43 of high voltage nodes 81, second cross valve 80 of the first tie point 101, second cross valve 80 of refrigerant flow direction converting 100, get back to again the second heat exchanger 4, so far complete the heat pump cycle of the single stage compress that once two compressors run simultaneously.
2) high pressure compressor 1 works, and low pressure compressor 2 does not work
Now, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70;
The high voltage nodes 81 of the second cross valve 80 communicates with the commutation node 82 of the second cross valve 80, and the low pressure node 83 of the second cross valve 80 communicates with the commutation node 84 of the second cross valve 80.
First throttle mechanism 5 normally works, and second throttle body 6 is closed, the 3rd throttle mechanism 9 standard-sized sheet.
Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 3 is as described below:
From the second heat exchanger 4 low-temperature low-pressure refrigerant gas out successively through the 44 pipeline 44, the commutation node 84 of the second cross valve 80, the low pressure node 83 of the second cross valve 80, second tie point 102 of refrigerant flow direction converting 100, 61 pipeline 61, second check valve 22 arrival end, second check valve 22 port of export, 64 pipeline 64, enter after high pressure compressor 1 compressed, again successively through the 63 pipeline 63, first tie point 101 of refrigerant flow direction converting 100, the high voltage nodes 81 of the second cross valve 80, the commutation node 82 of the second cross valve 80, First Heat Exchanger 3, 41 pipeline 41, 3rd throttle mechanism 9, liquid reservoir 7, 42 pipeline 42, first throttle mechanism 5, 43 pipeline 43, get back to again the second heat exchanger 4, so far the heat pump cycle of the single stage compress of a high pressure compressor 1 isolated operation is completed.
When working under this scenario, the port of export of low pressure compressor 2 and the refrigerant pressure of arrival end are consistent, under being all in the pressure of inspiration(Pi) of high pressure compressor 1.
(2) Two-stage Compression operating condition (First Heat Exchanger 3 is to user's heat supply)
Under this operating mode, high pressure compressor 1, low pressure compressor 2 all work, and are in series connection.During work, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70;
The high voltage nodes 81 of the second cross valve 80 communicates with the commutation node 82 of the second cross valve 80, and the low pressure node 83 of the second cross valve 80 communicates with the commutation node 84 of the second cross valve 80.
3rd throttle mechanism 9 standard-sized sheet.
First throttle mechanism 5, second throttle body 6 all normally work, and first throttle mechanism 5, for the throttling of refrigerant liquid, controls the refrigerant flow by the second heat exchanger 4; Second throttle body 6 for controlling the air compensation in Two-stage Compression process, thus controls the delivery temperature of intermediate pressure or high pressure compressor 1; Usually when second throttle body 6 be connected with the fluid space of liquid reservoir 7 time, be controlled by the delivery temperature of mode to the intermediate pressure in Two-stage Compression process or high pressure compressor 1 of hydrojet; When second throttle body 6 be connected with the gas compartment of liquid reservoir 7 time, be controlled by the delivery temperature of jet mode to the intermediate pressure in Two-stage Compression process or high pressure compressor 1.
Under this operating condition, the workflow of heat-pump apparatus shown in Fig. 3 is as described below:
From First Heat Exchanger 3 refrigerant liquid out, successively through the 41 pipeline 41, the 3rd throttle mechanism 9, enter liquid reservoir 7 and be divided into two-way; First via cold-producing medium is successively through the low pressure node 83 of commutation node 84, second cross valve 80, second tie point the 102, the 61 pipeline 61 of refrigerant flow direction converting 100 of the 42 pipeline 42, first throttle mechanism the 5, the 43 pipeline 43, second heat exchanger the 4, the 44 pipeline 44, second cross valve 80, enter after low pressure compressor 2 compressed by the first order, again successively through commutation node the 74, the 65 pipeline 65 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, enter the 64 pipeline 64; Second road cold-producing medium, successively through the 45 pipeline 45, second throttle body 6, blowdown pipe 46, also enters the 64 pipeline 64; Two-way cold-producing medium is after the 64 pipeline 64 mixes, enter high pressure compressor 1 again to be compressed by the second level, and then successively through the commutation node 82 of high voltage nodes 81, second cross valve 80 of the first tie point 101, second cross valve 80 of the 63 pipeline 63, refrigerant flow direction converting 100, get back to again First Heat Exchanger 3, so far complete the two-stage compression heat pump circulation of a sub-band second vapor injection.
(3) single stage compress operating condition (First Heat Exchanger 3 is to user's cooling)
Under this operating mode, high pressure compressor 1, low pressure compressor 2 are in parallel connection.During work, there is following operating scheme.
1) high pressure compressor 1, low pressure compressor 2 work simultaneously
Now, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70;
The high voltage nodes 81 of the second cross valve 80 communicates with the commutation node 84 of the second cross valve 80, and the low pressure node 83 of the second cross valve 80 communicates with the commutation node 82 of the second cross valve 80.
First throttle mechanism 5 standard-sized sheet, second throttle body 6 is closed, and the 3rd throttle mechanism 9 normally works.
Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 3 is as described below:
From First Heat Exchanger 3 low-temperature low-pressure refrigerant gas out successively through the low pressure node 83 of commutation node 82, second cross valve 80, second tie point 102 of refrigerant flow direction converting 100 of the second cross valve 80, enter the 61 pipeline 61 and be divided into two-way; The first via, successively through the second check valve 22 arrival end, second check valve 22 port of export, the 64 pipeline 64, enters after high pressure compressor 1 compressed, then is discharged into the 63 pipeline 63; Second tunnel enters after low pressure compressor 2 compressed, again successively through commutation node 72, first check valve 21 arrival end, first check valve 21 port of export, the 62 pipeline 62 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, be also discharged into the 63 pipeline 63; Two-way gas is after the 63 pipeline 63 mixes, again successively through commutation node the 84, the 44 pipeline 44, second heat exchanger the 4, the 43 pipeline 43, first throttle mechanism the 5, the 42 pipeline 42, liquid reservoir 7, the 3rd throttle mechanism the 9, the 41 pipeline 41 of high voltage nodes 81, second cross valve 80 of the first tie point 101, second cross valve 80 of refrigerant flow direction converting 100, get back to again First Heat Exchanger 3, so far complete the kind of refrigeration cycle of the single stage compress that once two compressors run simultaneously.
2) high pressure compressor 1 works, and low pressure compressor 2 does not work
Now, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70;
The high voltage nodes 81 of the second cross valve 80 communicates with the commutation node 84 of the second cross valve 80, and the low pressure node 83 of the second cross valve 80 communicates with the commutation node 82 of the second cross valve 80.
First throttle mechanism 5 standard-sized sheet, second throttle body 6 is closed, and the 3rd throttle mechanism 9 normally works.
Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 3 is as described below:
From First Heat Exchanger 3 low-temperature low-pressure refrigerant gas out successively through the commutation node 82 of the second cross valve 80, the low pressure node 83 of the second cross valve 80, second tie point 102 of refrigerant flow direction converting 100, 61 pipeline 61, second check valve 22 arrival end, second check valve 22 port of export, 64 pipeline 64, enter after high pressure compressor 1 compressed, again successively through the 63 pipeline 63, first tie point 101 of refrigerant flow direction converting 100, the high voltage nodes 81 of the second cross valve 80, the commutation node 84 of the second cross valve 80, 44 pipeline 44, second heat exchanger 4, 43 pipeline 43, first throttle mechanism 5, 42 pipeline 42, liquid reservoir 7, 3rd throttle mechanism 9, 41 pipeline 41, get back to again First Heat Exchanger 3, so far the kind of refrigeration cycle of the single stage compress of a high pressure compressor 1 isolated operation is completed.
When working under this scenario, the port of export of low pressure compressor 2 and the refrigerant pressure of arrival end are consistent, under being all in the pressure of inspiration(Pi) of high pressure compressor 1.
Embodiment 4
As shown in Figure 4, the difference of heat-pump apparatus shown in it and embodiment 3 Fig. 3 is: in the heat-pump apparatus shown in the present embodiment Fig. 4, adds the 3rd check valve 23; 3rd check valve 23 connected mode is in systems in which: the arrival end of the 3rd check valve 23 is connected with the port of export of high pressure compressor 1, and the port of export of the 3rd check valve 23 is connected with the 62 pipeline 62 with the 63 pipeline 63.
In the course of work, heat-pump apparatus shown in the present embodiment Fig. 4 is except realizing all operating conditions of heat-pump apparatus shown in the utility model embodiment 3 Fig. 3, and beyond all operating schemes under all operating conditions, following operating scheme can also be realized for single stage compress operating condition, that is: high pressure compressor 1 does not work, the operating scheme that low pressure compressor 2 works.
(1) high pressure compressor 1 does not work, the single stage compress heat supply running scheme that low pressure compressor 2 works
Under this operating scheme, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70;
The high voltage nodes 81 of the second cross valve 80 communicates with the commutation node 82 of the second cross valve 80, and the low pressure node 83 of the second cross valve 80 communicates with the commutation node 84 of the second cross valve 80.
First throttle mechanism 5 normally works, and second throttle body 6 is closed, the 3rd throttle mechanism 9 standard-sized sheet.
Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 4 is as described below:
From the second heat exchanger 4 low-temperature low-pressure refrigerant gas out successively through the 44 pipeline 44, the commutation node 84 of the second cross valve 80, the low pressure node 83 of the second cross valve 80, second tie point 102 of refrigerant flow direction converting 100, 61 pipeline 61, enter after low pressure compressor 2 compressed, again successively through the high voltage nodes 71 of the first cross valve 70, the commutation node 72 of the first cross valve 70, first check valve 21 arrival end, first check valve 21 port of export, 62 pipeline 62, 63 pipeline 63, first tie point 101 of refrigerant flow direction converting 100, the high voltage nodes 81 of the second cross valve 80, the commutation node 82 of the second cross valve 80, First Heat Exchanger 3, 41 pipeline 41, 3rd throttle mechanism 9, liquid reservoir 7, 42 pipeline 42, first throttle mechanism 5, 43 pipeline 43, get back to again the second heat exchanger 4, so far the heat pump cycle of the single stage compress of a low pressure compressor 2 isolated operation is completed.
(2) high pressure compressor 1 does not work, the single stage compress refrigerating operaton scheme that low pressure compressor 2 works
Under this operating scheme, the high voltage nodes 71 of the first cross valve 70 communicates with the commutation node 72 of the first cross valve 70, and the low pressure node 73 of the first cross valve 70 communicates with the commutation node 74 of the first cross valve 70;
The high voltage nodes 81 of the second cross valve 80 communicates with the commutation node 84 of the second cross valve 80, and the low pressure node 83 of the second cross valve 80 communicates with the commutation node 82 of the second cross valve 80.
First throttle mechanism 5 standard-sized sheet, second throttle body 6 is closed, and the 3rd throttle mechanism 9 normally works.
Under this operating scheme, the workflow of heat-pump apparatus shown in Fig. 4 is as described below:
From First Heat Exchanger 3 low-temperature low-pressure refrigerant gas out successively through the commutation node 82 of the second cross valve 80, the low pressure node 83 of the second cross valve 80, second tie point 102 of refrigerant flow direction converting 100, 61 pipeline 61, enter after low pressure compressor 2 compressed, again successively through the high voltage nodes 71 of the first cross valve 70, the commutation node 72 of the first cross valve 70, first check valve 21 arrival end, first check valve 21 port of export, 62 pipeline 62, 63 pipeline 63, first tie point 101 of refrigerant flow direction converting 100, the high voltage nodes 81 of the second cross valve 80, the commutation node 84 of the second cross valve 80, 44 pipeline 44, second heat exchanger 4, 43 pipeline 43, first throttle mechanism 5, 42 pipeline 42, liquid reservoir 7, 3rd throttle mechanism 9, 41 pipeline 41, get back to again First Heat Exchanger 3, so far the kind of refrigeration cycle of the single stage compress of a low pressure compressor 2 isolated operation is completed.
Embodiment 5
For the heat-pump apparatus shown in the utility model embodiment 1 Fig. 1, by increasing an intercooler in its system, can be improved further it.This intercooler has four connectors, respectively: exhaust entrance, air exit, cooling refrigeration agent entrance, cooling refrigeration agent outlet.
The connected mode of this intercooler in the heat-pump apparatus shown in Fig. 1 is: the exhaust entrance of intercooler is connected with the 65 pipeline 65; The air exit of intercooler is connected with the 64 pipeline 64; The cooling refrigeration agent entrance of intercooler is connected with liquid reservoir 7 by blowdown pipe 46, second throttle body the 6, the 45 pipeline 45 successively; The cooling refrigeration agent outlet of intercooler can with the 65 pipeline 65, intercooler air exit place pipeline, or any place's pipeline among the 64 pipeline 64 is connected.
The effect of intercooler in the heat-pump apparatus shown in Fig. 1 is: when the heat-pump apparatus shown in Fig. 1 works under Two-stage Compression operating condition, First Heat Exchanger 3 is as condenser, during for the production of hot water, the exhaust of intercooler to low pressure compressor 2 is utilized to cool.
Its workflow is as described below respectively.
Scheme one: when the cooling refrigeration agent outlet of intercooler is connected with the 65 pipeline 65
Its workflow is: from a part of refrigerant liquid of liquid reservoir 7 after second throttle body 6 throttling, become the refrigerant air-liquid two-phase mixture of medium temperature and medium pressure, successively by the cooling refrigeration agent entrance of blowdown pipe 46, intercooler, enter in intercooler, carry out indirect heat exchange with the refrigerant gas from intercooler exhaust entrance; In intercooler, after the refrigerant air-liquid two-phase mixture heat absorption of medium temperature and medium pressure, become the refrigerant gas of medium temperature and medium pressure, then enter in the 65 pipeline 65 through the cooling refrigeration agent outlet of intercooler; With from low pressure compressor 2 port of export, and successively through the commutation node 74 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, after the low pressure compressor 2 also entered in the 65 pipeline 65 is vented mixing, enter the exhaust entrance of intercooler; From the refrigerant gas of intercooler exhaust entrance in intercooler, after the cooling of the refrigerant air-liquid two-phase mixture of medium temperature and medium pressure, then enter in the 64 pipeline 64 through intercooler air exit.
Scheme two: when the cooling refrigeration agent outlet of intercooler is connected with the pipeline at intercooler air exit place
Its workflow is: from a part of refrigerant liquid of liquid reservoir 7 after second throttle body 6 throttling, become the refrigerant air-liquid two-phase mixture of medium temperature and medium pressure, successively by the cooling refrigeration agent entrance of blowdown pipe 46, intercooler, enter in intercooler, with from low pressure compressor 2 port of export, and successively through commutation node the 74, the 65 pipeline 65 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, indirect heat exchange is carried out in the exhaust of the low pressure compressor 2 entered in intercooler by intercooler exhaust entrance; In intercooler, after the refrigerant air-liquid two-phase mixture heat absorption of medium temperature and medium pressure, become the refrigerant gas of medium temperature and medium pressure, the cooling refrigeration agent outlet through intercooler enters in the air exit place pipeline of intercooler; And after cooled device, also enter in the air exit place pipeline of intercooler by the air exit of intercooler from the exhaust of low pressure compressor 2 in intercooler; After mixing with the medium temperature and medium pressure refrigerant gas exported from the agent of intercooler cooling refrigeration, enter in the 64 pipeline 64.
Scheme three: when the cooling refrigeration agent outlet of intercooler is connected with the 64 pipeline 64
Its workflow is: from a part of refrigerant liquid of liquid reservoir 7 after second throttle body 6 throttling, become the refrigerant air-liquid two-phase mixture of medium temperature and medium pressure, successively by the cooling refrigeration agent entrance of blowdown pipe 46, intercooler, enter in intercooler, with from low pressure compressor 2 port of export, and successively through commutation node the 74, the 65 pipeline 65 of high voltage nodes 71, first cross valve 70 of the first cross valve 70, indirect heat exchange is carried out in low pressure compressor 2 exhaust entered in intercooler by the exhaust entrance of intercooler; In intercooler, after the refrigerant air-liquid two-phase mixture heat absorption of medium temperature and medium pressure, become the refrigerant gas of medium temperature and medium pressure, the cooling refrigeration agent outlet through intercooler enters in the 64 pipeline 64; And after cooled device, successively by the air exit of intercooler, the air exit place pipeline of intercooler, also enter in the 64 pipeline 64 from the exhaust of low pressure compressor 2 in intercooler; After mixing with the medium temperature and medium pressure refrigerant gas exported from the agent of intercooler cooling refrigeration, then enter high pressure compressor 1 and compressed by the second level.
The above scheme of embodiment 5 and operation principle are also applicable to embodiment 2,3,4.
In the scheme of the above-mentioned all embodiments of the utility model, in described low pressure compressor 2, high pressure compressor 1 any one or all, can adopt in following compressor any one: screw compressor, helical-lobe compressor, rolling rotor compressor, sliding-vane compressor, rotary blade type compressor, centrifugal compressor, digital scroll compressor; In low pressure compressor 1, high pressure compressor 2 any one or all, also can be variable conpacitance compressor (such as: frequency-changeable compressor), or constant speed compressor.
In the scheme of the above-mentioned all embodiments of the utility model, any one or all in the first described check valve 21, second check valve 22, the 3rd check valve 23 can be had the by-pass valve control of turn-off function substitute, as magnetic valve etc.
In the scheme of the above-mentioned all embodiments of the utility model, the first described cross valve 70, second four-way 80 can adopt three court cards air-conditioning cross valves usually, blue Ke's air-conditioning cross valve, Ai Mosheng air-conditioning cross valve, open empty profit and adjust cross valve, China's aigret air-conditioning cross valve, any one in shield peace air-conditioning cross valve.
Claims (8)
1. a refrigerant flow direction converting, comprises high pressure compressor (1), low pressure compressor (2), the first check valve (21), the second check valve (22); It is characterized in that: this refrigerant flow direction converting also comprises the first cross valve (70);
The low pressure node (73) of described first cross valve (70) is connected with second tie point (102) of refrigerant flow direction converting by the 61 pipeline (61), the high voltage nodes (71) of described first cross valve (70) is successively through the port of export of described low pressure compressor (2), the arrival end of low pressure compressor (2) is connected with the 61 pipeline (61), first tie point (101) of refrigerant flow direction converting is successively through the 63 pipeline (63), the port of export of described high pressure compressor (1), the arrival end of high pressure compressor (1), 64 pipeline (64), described second check valve (22) port of export, second check valve (22) arrival end is connected with the 61 pipeline (61), any one node (72) in described first cross valve (70) two commutation node is successively through described first check valve (21) arrival end, first check valve (21) port of export, 62 pipeline (62) is connected with the 63 pipeline (63), another commutation node (74) of described first cross valve (70) is connected by the 64 pipeline (64) between the arrival end of the 65 pipeline (65) and described high pressure compressor (1) and the second check valve (22) port of export.
2. refrigerant flow direction converting according to claim 1, it is characterized in that the arrival end of the 3rd check valve (23) is connected with the port of export of described high pressure compressor (1), the port of export of described 3rd check valve (23) is connected with the 62 pipeline (62) with the 63 pipeline (63).
3. refrigerant flow direction converting according to claim 1, it is characterized in that the high voltage nodes (81) of the second cross valve (80) is connected with first tie point (101) of described refrigerant flow direction converting, the low pressure node (83) of described second cross valve (80) is connected with second tie point (102) of described refrigerant flow direction converting.
4. refrigerant flow direction converting according to claim 3, it is characterized in that the arrival end of the 3rd check valve (23) is connected with the port of export of described high pressure compressor (1), the port of export of described 3rd check valve (23) is connected with the 62 pipeline (62) with the 63 pipeline (63).
5. the refrigerant flow direction converting according to claim arbitrary in Claims 1-4, it is characterized in that blowdown pipe (46) one end is connected with second throttle body (6), blowdown pipe (46) other end is connected with the 64 pipeline (64) or the 65 pipeline (65).
6. the refrigerant flow direction converting according to claim arbitrary in Claims 1-4, is characterized in that the exhaust entrance of intercooler is connected with the 65 pipeline (65); The air exit of described intercooler is connected with the 64 pipeline (64); The cooling refrigeration agent entrance of described intercooler is connected with second throttle body (6) by blowdown pipe (46); The cooling refrigeration agent outlet of described intercooler is connected with the 65 pipeline (65).
7. the refrigerant flow direction converting according to claim arbitrary in Claims 1-4, is characterized in that the exhaust entrance of intercooler is connected with the 65 pipeline (65); The air exit of described intercooler is connected with the 64 pipeline (64); The cooling refrigeration agent entrance of described intercooler is connected with second throttle body (6) by blowdown pipe (46); The cooling refrigeration agent outlet of described intercooler is connected with the air exit place pipeline of described intercooler.
8. the refrigerant flow direction converting according to claim arbitrary in Claims 1-4, is characterized in that the exhaust entrance of intercooler is connected with the 65 pipeline (65); The air exit of described intercooler is connected with the 64 pipeline (64); The cooling refrigeration agent entrance of described intercooler is connected with second throttle body (6) by blowdown pipe (46); The cooling refrigeration agent outlet of described intercooler is connected with the 64 pipeline (64).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420437932.8U CN204141904U (en) | 2014-07-30 | 2014-07-30 | Refrigerant flow direction converting |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201420437932.8U CN204141904U (en) | 2014-07-30 | 2014-07-30 | Refrigerant flow direction converting |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104121729A (en) * | 2014-07-30 | 2014-10-29 | 刘雄 | Refrigerating fluid flowing direction conversion device |
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2014
- 2014-07-30 CN CN201420437932.8U patent/CN204141904U/en not_active Withdrawn - After Issue
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104121729A (en) * | 2014-07-30 | 2014-10-29 | 刘雄 | Refrigerating fluid flowing direction conversion device |
| CN104121729B (en) * | 2014-07-30 | 2017-02-15 | 刘雄 | Refrigerating fluid flowing direction conversion device |
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