CN115013317A

CN115013317A - Vortex assembly, vortex compressor and compressor heat pump system

Info

Publication number: CN115013317A
Application number: CN202210853237.9A
Authority: CN
Inventors: 曾荡; 王蒙
Original assignee: Emerson Climate Technologies Suzhou Co Ltd
Current assignee: Copeland Suzhou Co Ltd
Priority date: 2017-03-23
Filing date: 2017-03-23
Publication date: 2022-09-06
Also published as: CN108626905A

Abstract

The invention relates to a scroll assembly, a scroll compressor and a compressor heat pump system. The compressor heat pump system includes: a compressor having two discharge paths independent of each other provided by a scroll assembly of the compressor; two condensers connected to the two exhaust paths of the compressor, respectively; an evaporator disposed downstream of the condensers and connected to the two condensers. The vortex subassembly includes the fixed vortex and the vortex that move that cooperate each other in order to compress working fluid, and the fixed vortex includes first fixed vortex blade and second fixed vortex blade, moves the vortex and includes first movable vortex blade and second movable vortex blade, and the fixed vortex is injectd first compression chamber group and second compression chamber group independent each other with the cooperation of moving the vortex. The scroll assembly is provided with two discharge ports respectively communicating with the first compression chamber group and the second compression chamber group to provide two discharge paths. At least one of the first compression pocket set and the second compression pocket set provides a pressure ratio equal to a system pressure ratio of the compressor heat pump system.

Description

Vortex assembly, vortex compressor and compressor heat pump system

The application is a divisional application of an invention patent application with the application date of 2017, 3 and 23, and the application number of 201710179183.1, and the invention name of the invention is 'scroll component, scroll compressor and compressor heat pump system'.

Technical Field

The present invention relates to scroll apparatus and related heat pump systems, and in particular to scroll assemblies, scroll compressors including the same, and related compressor heat pump systems.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

A Heat Pump system (Heat Pump) is a system that transfers Heat energy of a low-level Heat source to a high-level Heat source, and a Heat Pump generally obtains low-level Heat energy from air, water or soil in the nature, applies work by electric power, and then provides the high-level Heat energy that can be utilized for people. The compressor heat pump system is a heat pump system widely used at present, and generally comprises four parts: a compressor, a condenser, a throttle valve, and an evaporator. The basic operation of the compressor heat pump system is as follows: the compressor sucks refrigerant (such as Freon), sucked refrigerant gas is compressed into high-temperature and high-pressure refrigerant vapor in the compressor, the high-temperature and high-pressure refrigerant gas is cooled and condensed into medium-temperature and high-pressure refrigerant liquid by low-temperature fluid (such as water or air) in the condenser, the refrigerant releases heat to heat the low-temperature fluid in the process, the medium-temperature and high-pressure refrigerant liquid flows out of the condenser and is throttled into low-temperature and low-pressure liquid refrigerant by throttling elements (such as capillary tubes, expansion valves and the like), the low-temperature and low-pressure liquid refrigerant enters the evaporator, the high-temperature fluid (such as normal-temperature air) absorbs heat in the evaporator and is gasified into high-temperature and low-pressure vapor, so that a working cycle is completed, and the low-pressure high-temperature vapor is sucked into the compressor again to continue to carry out the next working cycle.

A simplified schematic of a single compressor heat pump system 100' is shown in fig. 1, which essentially comprises: a compressor 110 ', a condenser 120', an evaporator 130 ', and a throttle valve 140'. As shown in the figure, in the single compressor heat pump system 100 ', a condenser 120 ' is generally connected to the working circuit of the compressor 110 ', and the high temperature refrigerant from the compressor 110 ' releases heat in the condenser 120 ' to heat the working fluid therein to a desired temperature and supply the heated working fluid to an environment requiring heat supply. Thus, a single compressor heat pump system can generally only provide a working fluid having a single temperature.

In practical applications, the temperature requirements of different working environments are different. If it is desired to provide working fluids of different temperatures by a single compressor heat pump system, one currently employed method is to mix the working fluid provided by the condenser at a predetermined temperature with additional cryogenic fluid (which may also be a high temperature fluid) to thereby obtain working fluids of different temperatures to meet the requirements of different environments. This approach can result in wasted heat and increased system complexity.

Therefore, there is a need for an improved solution.

Disclosure of Invention

It is an object of the present invention to provide a compressor heat pump system that provides multiple discharge paths by improving the structure of the scroll assembly.

It is a further object of the present invention to provide a scroll assembly and associated scroll compressor which is provided with a plurality of discharge ports so as to be capable of providing a plurality of discharge gas paths.

One or more of the above objects can be achieved by the following aspects.

According to one aspect of the present disclosure, there is provided a compressor heat pump system, comprising: a compressor having two discharge paths independent of each other provided by a scroll assembly of the compressor; two condensers arranged downstream of the compressor and connected to two exhaust paths of the compressor, respectively; an evaporator disposed downstream of the condensers and connected to the two condensers; the vortex assembly comprises a fixed vortex and an orbiting vortex which are matched with each other to compress a working fluid, the fixed vortex comprises a first fixed vortex blade and a second fixed vortex blade, the orbiting vortex comprises a first orbiting vortex blade and a second orbiting vortex blade, and the fixed vortex and the orbiting vortex are matched to define a first compression cavity group and a second compression cavity group which are independent from each other; and wherein the scroll assembly is provided with two discharge ports communicating with the first and second compression chamber groups, respectively, to provide two discharge paths.

According to the scheme, the design of the compression cavity group of the scroll assembly and the arrangement of the exhaust ports are improved, so that the compressor can provide two independent exhaust paths (even more paths) by itself, two (even more) condensers can be driven to work, the structure of a heat pump system does not need to be changed, and additional medium mixing equipment does not need to be equipped.

Preferably, two exhaust ports are formed on an end plate of the non-orbiting scroll or the orbiting scroll.

Preferably, the two discharge ports are directly communicated with the first discharge port of the first compression chamber group and the second discharge port of the second compression chamber group, respectively.

Preferably, the two exhaust ports are formed on an additional cover plate located at an upper portion of the scroll assembly.

Preferably, two discharge chambers located below the two discharge ports are formed in the end plate of the fixed scroll, and the two discharge ports are respectively communicated with the first discharge port of the first compression chamber group and the second discharge port of the second compression chamber group via the two discharge chambers.

Preferably, a modulation passage below the discharge chamber is further formed in the end plate of the non-orbiting scroll, the modulation passage opens into one or more compression chambers of the first compression chamber group and/or the second compression chamber group and an opening thereof in the discharge chamber is covered by a check valve.

Preferably, each of the two discharge ports extends to the housing of the compressor and has an opening to the outside formed on the housing of the compressor.

Preferably, the head space of the compressor is divided into two discharge chambers independent of each other, and the two discharge ports are respectively opened to the respective discharge chambers.

Preferably, the exterior of each discharge chamber is provided with a discharge connection for connecting a condenser.

Preferably, the first compression chamber group and the second compression chamber group have the same capacity.

Preferably, the first compression chamber group and the second compression chamber group have different capacities.

Preferably, the profile length of the first orbiting scroll blade (121) is greater than the profile length of the second orbiting scroll blade (122), or the profile height of the first orbiting scroll blade is greater than the profile height of the second orbiting scroll blade.

Preferably, at least one of the first compression chamber group and the second compression chamber group provides a pressure ratio equal to a system pressure ratio of the compressor heat pump system.

Preferably, the condensers have different nominal operating pressures.

According to another aspect of the present disclosure, there is also provided a scroll assembly including an orbiting scroll and a non-orbiting scroll cooperating with each other to compress a working fluid, wherein the non-orbiting scroll includes a first non-orbiting scroll blade and a second non-orbiting scroll blade, the orbiting scroll includes a first orbiting scroll blade and a second orbiting scroll blade, and the non-orbiting scroll and the orbiting scroll cooperate to define a first compression chamber group and a second compression chamber group independent from each other; wherein the scroll assembly is provided with two discharge ports respectively communicating with the first compression chamber group and the second compression chamber group to provide two discharge paths.

Preferably, the two discharge ports are in direct communication with the first discharge port of the first compression pocket set and the second discharge port of the second compression pocket set, respectively.

Preferably, the cover plate includes two discharge chambers located below the two discharge ports, and the two discharge ports are respectively communicated with the first discharge port of the first compression chamber group and the second discharge port of the second compression chamber group via the two discharge chambers.

Preferably, a modulation passage communicating two discharge ports with the first and second compression chamber groups is formed in an end plate of the fixed scroll or the movable scroll, the modulation passage opens to one or more compression chambers of the first compression chamber group and/or the second compression chamber group and an opening thereof in the discharge chamber is covered by a check valve.

According to an aspect of the present disclosure there is provided a scroll compressor including a scroll assembly according to the preceding aspect of the present disclosure.

Drawings

The features and advantages of one or more embodiments of the present invention will become more readily understood from the following description taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a schematic diagram of a compressor heat pump system of the prior art;

FIG. 2 is a schematic diagram of a compressor heat pump system according to an embodiment of the present invention;

FIG. 3 is a cross-sectional view of a scroll assembly according to an embodiment of the present invention;

FIG. 4 is a longitudinal cross-sectional view of a scroll assembly according to an embodiment of the present invention;

FIG. 5 is a top view of the scroll assembly from above the non-orbiting scroll according to an embodiment of the present invention;

FIG. 6 is a schematic view of an orbiting scroll of a scroll assembly according to an embodiment of the present invention;

FIG. 7 is a schematic view of an orbiting scroll of a scroll assembly according to another embodiment of the present invention;

FIG. 8 is a schematic view of an orbiting scroll of a scroll assembly according to yet another embodiment of the present invention;

FIG. 9 is a schematic view of a non-orbiting scroll of a scroll assembly according to one embodiment of the present invention; and

FIG. 10 is a schematic illustration of a non-orbiting scroll of a scroll assembly according to another embodiment of the present invention.

Detailed Description

The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. The same reference numerals are used to designate the same components in the respective drawings, and thus the configurations of the same components will not be described repeatedly.

Before describing the embodiments of the present invention, a brief description will be given of the basic technical concept of the present invention.

As previously explained in the background, if it is desired to provide working fluids of different temperatures for different environments of use, it has been the practice to provide working fluids of different temperatures by mixing additional fluids or adding compressor-condenser banks. The existing methods, which have been initiated by providing an additional fluid supply to the heat pump system or increasing the working circuit of the heat pump system, may complicate the structure of the system and may result in waste of heat.

The present invention adopts different technical concepts. In order to avoid the structure of the heat pump system from becoming complicated, the present invention contemplates improving the structure of the compressor itself so that the compressor itself provides a plurality of discharge paths for supplying compressed gas to a plurality of condensers. This allows a single compressor to operate with multiple condensers without having to equip each condenser with a compressor and without using additional mixing equipment. The present inventors have attempted to overcome the difficulties in design and to improve the existing structure of the compressor in order to provide working fluids of different temperatures in a more simplified heat pump system structure by expanding the function of the compressor.

The design of a compressor heat pump system and associated scroll assembly and scroll compressor according to embodiments of the present invention will now be described with reference to figures 2 to 9.

Fig. 2 shows a simplified schematic of a compressor heat pump system 10 according to an embodiment of the present invention. The compressor heat pump system 10 in fig. 2 includes: a compressor 100, two

condensers

210, 220 arranged downstream of the compressor 100, and an evaporator 300 arranged downstream of and connected to the

condensers

210, 220. As shown in fig. 2, the compressor 100 provides two

discharge paths

101, 102 independent of each other, each

discharge path

101, 102 being connected to a

respective condenser

210, 220 for supplying compressed gas thereto.

It should be noted that fig. 2 only shows some basic components of the heat pump system 10 according to the present invention, and the actual heat pump system is extended based on this simplified system. For example, a corresponding number of condensers may be provided depending on the number of discharge paths that the compressor 100 is capable of providing. In addition, other equipment such as fluid recovery equipment, fluid purification equipment, etc. may be provided. In fig. 2, a

throttle valve

410, 420 is shown in each circulation path, which is primarily used for throttling and converting the medium temperature and high pressure working fluid from the

condensers

210, 220 to medium temperature and medium pressure working fluid. In case the nominal operating temperature (nominal operating pressure) of the two

condensers

210, 220 is different, a check valve may also be arranged downstream of the

condensers

210, 220 to prevent fluid from streaming into the adjacent working path.

According to the concept of the embodiment of the present invention, a plurality of discharge paths are provided by changing the structure of the compressor 100. The manner in which the scroll assembly is modified to provide multiple exhaust paths will now be described with reference to the accompanying drawings and specific examples.

Fig. 3 and 4 illustrate a transverse cross-sectional view and a longitudinal cross-sectional view, respectively, of a scroll assembly of the compressor 100, according to one embodiment. In this embodiment, the scroll assembly is configured as a double-wrap scroll assembly 110. In the illustrated double-orbiting scroll assembly 110, the non-orbiting scroll 130 and the orbiting scroll 120 each have two scroll blades. The non-orbiting scroll 130 includes first and second

non-orbiting scroll blades

131 and 132, and the orbiting scroll 120 includes first and second

orbiting scroll blades

121 and 122. The first orbiting scroll blade 121 is meshingly engaged with the first and second

non-orbiting scroll blades

131 and 132, respectively, to form a first compression chamber group C1. The first compression chamber group C1 may include a sub compression chamber C1A located radially inward of the first orbiting scroll blade 121 and a sub compression chamber C1B located radially outward of the first orbiting scroll blade 121. Similarly, the second orbiting scroll blade 122 meshingly engages with the first and second

non-orbiting scroll blades

131 and 132, respectively, to form a second compression chamber group C2. The second compression chamber group C2 may include a sub compression chamber C2A located radially inward of the second orbiting scroll blade 132 and a sub compression chamber C1B located radially outward of the second orbiting scroll blade 132. The first compression pocket set C1 and the second compression pocket set C2 perform compression operations independently of each other and include respective intake and exhaust sections. Specifically, a first discharge hole O1 and a second discharge hole O2 corresponding to the first compression chamber group C1 and the second compression chamber group C2, respectively, may be provided on the non-orbiting scroll end plate 133 of the non-orbiting scroll 130 to discharge high-pressure gas compressed by the first compression chamber group C1 and the second compression chamber group C2, respectively. Each of the first compression pocket set C1 and the second compression pocket set C2 (or more specifically each of the sub-compression pockets) may include a low pressure pocket located generally radially outward and at suction pressure, a high pressure pocket located generally radially inward and at discharge pressure, and an intermediate pressure pocket having a pressure intermediate therebetween, respectively. As the compressor is operated, the low-pressure region located at the radially outermost side gradually moves from the radially outer side to the radially intermediate portion in the profile direction of the scroll blade to become a medium-pressure chamber, and then further moves to the radially inner side in the profile direction to become a high-pressure chamber, and finally is discharged from the corresponding discharge hole.

Further, as shown in FIG. 4, the scroll assembly 110 is also provided with two

discharge ports

143 and 144, the two

discharge ports

143, 144 communicating with the first compression pocket set C1 and the second compression pocket set C2, respectively, to provide two independent discharge paths. Specifically, in the example of fig. 4, two

exhaust ports

143, 144 are formed in cover plate 140 disposed above non-orbiting scroll 130, opening into first and second compression pocket sets C1, C2, respectively. Also, as shown in the drawing, both the

exhaust ports

143, 144 are formed as cylindrical members.

The above-described embodiments according to the present invention provide two independent discharge paths by improving the structure of the scroll assembly, i.e., configuring the scroll assembly to provide two independent compression chamber groups, thereby providing independent discharge ports communicating with the two compression chamber groups. Thus, the number of discharge paths that the compressor 100 can provide is increased, enabling one compressor 100 to operate with two (or even more)

condensers

210, 220, so that two working fluids of different temperatures can be provided through the two

condensers

210, 220.

It should be understood that the example of fig. 4 is not limiting, and that the

exhaust ports

143, 144 may be otherwise arranged. For example, in an embodiment not shown, the exhaust port may be formed on the end plate 123 of the orbiting scroll 120 or the end plate 133 of the non-orbiting scroll 130. In this case, the two discharge ports may directly communicate with the first discharge port O1 of the first compression chamber group C1 and the second discharge port O2 of the second compression chamber group C2, respectively. The first exhaust port O1 and the second exhaust port O2 are typically formed in the end plate 122 or the end plate 133. Thus, the compressed gas from the first compression pocket C1 and the second compression pocket C2 can be discharged to the

downstream condensers

210, 220 through the gas discharge ports O1 and O2 and the corresponding

gas discharge ports

143, 144, independently of each other.

Also, while the scroll assembly 110 is shown in FIG. 4 as being provided with two

discharge ports

143, 144, it should be understood that the number of discharge ports need not be two — that is, corresponding to the number of compression pocket sets C1, C2 of the scroll assembly 110. According to other embodiments of the present invention, it may be considered to arrange more than two discharge ports to provide a corresponding number of discharge paths, as long as it is ensured that the discharge ports can communicate with the compression chamber group. In this case, the structure of the scroll assembly 110 may be relatively complicated, and accordingly, the parameter design of the compressor 100 may be relatively more complicated.

The structure of the scroll assembly 110 will be described next with reference to fig. 4. In the example of fig. 4, two

discharge chambers

135 and 136 are further formed on the top of the end plate 133 of the non-orbiting scroll 130, the two

discharge chambers

135 and 136 are located below the two

discharge ports

143 and 144, respectively, and the

discharge ports

143 and 144 communicate with the first and second compression chamber groups C1 and C2 below, specifically, the first and second discharge ports O1 and O2, via the two

discharge chambers

135 and 136. In this case, the compressed gas from the first compression pocket C1 and the second compression pocket C2 will be discharged independently to the

downstream condensers

210, 220 through the gas outlet ports O1 and O2, the respective

gas outlet chambers

135 and 136, and the respective

gas outlet ports

143, 144, respectively, in this order.

It should be noted that the

discharge chambers

135 and 136 on the non-orbiting scroll 130 are not only used to connect the

discharge ports

143 and 144 to the first and second compression banks C1 and C2, but also used as pressure accumulation chambers of compressed gas, and can be used for adaptation of discharge pressure by arranging additional members. The following description will be continued with reference to fig. 4 and 5.

Modulation passages are also formed in end plate 133 of non-orbiting scroll 130 according to the present disclosure, below

discharge chambers

135, 136, respectively, and opening into one or more sub-compression pockets of first and second compression pocket sets C1, C2, respectively. The two

discharge chambers

135, 136 are configured to receive compressed gas from the first compression pocket set C1 and the second compression pocket set C2 via respective modulation passages. In particular, the two

discharge chambers

135, 136 are capable of receiving gas from different pressure regions of the first compression chamber group C1 and the second compression chamber group C2, depending on the position of the modulation passage.

A top structure schematic of a non-orbiting scroll 130 according to an embodiment of the present disclosure is shown in fig. 5, wherein a specific arrangement of modulation passages is shown, by which compressed gas from different pressure regions of the first and second compression chamber groups C1 and C2 may be selectively received. As shown in the drawing, two

discharge chambers

135, 136 in the top of the end plate 133 of the non-orbiting scroll 130 are separated by a partition wall 134. In the area of the

outlet chambers

135, 136, three

modulation channels

137a, 137b, 137c and 138a, 138b, 138c are arranged in each case. Further, a check valve V is disposed above the

modulation passages

137a, 137b, 137c and 138a, 138b, 138 c. By this arrangement, it is possible to selectively receive compressed gas of different pressure regions. As previously described, the first and second compression pockets C1 and C2 each include a low pressure region, a medium pressure region, and a high pressure region from the radially outer side to the radially inner side of the scroll assembly 110, and to this end, the three modulation passages 137a/138a, 137b/138b, 137C/138C in each

discharge pocket

135, 136 may be arranged to communicate with regions of the compression pockets C1 and C2, respectively, at different pressures, so that gas having different pressures (different degrees of compression) from the different pressure regions may be received and the received gas may be discharged to the condenser 210 through the downstream discharge chamber 135 and discharge port 143. When the gas pressure from the compression pocket set C1, C2 below the check valve V is greater than the pressure in the

discharge pocket

135, 136 above the check valve V, the check valve V opens, allowing the pressure of the compression pocket set C1, C2 to enter the

discharge pocket

135, 136, thereby avoiding over-compression. However, when the gas pressure in the compression chamber group C1, C2 is equal to or less than the pressure in the

discharge chamber

135, 136, the check valve V remains closed.

The operation of the one-way valve V will now be described, taking as an example the discharge chamber 135 and its

corresponding modulation passages

137a, 137b, 137c and the one-way valve V, and the discharge chamber 136 and its

corresponding modulation passages

138a, 138b, 138c and its one-way valve V will operate in a similar manner.

If the rated operating pressure of the downstream condenser 210 is greater than the pressure at the first exhaust port O1 of the first compression pocket set C1, the exhaust valve at the first exhaust port O1 will close until the pressure of the gas at the first exhaust port O1 builds to the desired operating pressure of the condenser 210, and the gas exiting the first exhaust port O1 is discharged to the condenser 210 via the exhaust pocket 135 and the outlet port 143. Since the pressure accumulated in the discharge chamber 135 is greater than the pressure of each of the compression chambers of the compression chamber groups C1, C2, the three check valves V in the discharge chamber 135 are all kept closed and the compressed gas is discharged only through the first discharge port O1.

If the working pressure of the downstream condenser 210 substantially corresponds to the pressure of one of the compression chambers in the first compression chamber group C1, the corresponding check valve V in the modulation passage 137a-137C corresponding to the compression chamber is opened to discharge the gas in the compression chamber to the discharge chamber 135 and then to the condenser 210 without completely compressing the gas and discharging the gas through the first discharge port O1, so that the over-compression can be prevented and the performance of the compressor can be improved.

Further, in order to implement multiple discharge paths of the compressor 100, in addition to arranging the

independent discharge ports

143, 144 on the scroll assembly 110, the structure of other portions of the compressor 100 may need to be changed accordingly to constitute multiple independent discharge paths, according to the principles of the present disclosure.

For example, in one embodiment, both discharge

ports

143, 144 are extended up to the casing of the compressor 100, such that both discharge

ports

143, 144 have an opening (not shown) to the outside formed on the casing of the compressor 100. In this manner, two separate discharge paths are established from the scroll assembly 110 to the exterior of the compressor 100, and no modification to the head space of the compressor 100 and no additional connecting piping disposed therein are required. In this arrangement, the openings of the

discharge ports

143, 144 on the housing of the compressor 100 can simultaneously serve as inlets to the external discharge fitting.

Alternatively, in another embodiment, it may be considered to divide the head space of the compressor 100 into two discharge chambers independent of each other and to have each of the two

discharge ports

143, 144 open to the respective discharge chamber, whereby a plurality of discharge paths from the scroll assembly 110 to the outside of the compressor 100 may also be provided. This arrangement, which is primarily directed to a modification of the head space of the compressor 100, requires that the discharge chambers be non-fluid communication with each other, thereby enabling independent discharge paths. Fig. 2 schematically shows a modification of the head space of the compressor 100, showing the top of the compressor 100 divided into two separate discharge chambers, and connected with

lines

101, 102, respectively.

After establishing the discharge path from the scroll assembly 110 to the outside of the compressor 100, a discharge joint for connecting the

condensers

210, 220 may be disposed on the casing of the compressor 100 in order to facilitate connection with the

condensers

210, 220. In the case where the

discharge ports

143, 144 extend to the casing of the compressor 100, a discharge joint may be disposed at an opening of the

discharge ports

143, 144 on the casing of the compressor 100; alternatively, in the case where the head space of the compressor 100 is divided into a plurality of discharge chambers, the discharge joint may be disposed outside each discharge chamber.

In addition, FIG. 4 also shows that two

back pressure chambers

141, 142 are formed at the top of the coverplate 140 of the scroll assembly 110. The two

back pressure chambers

141, 142 may communicate with one of the first compression chamber group C1 and one of the second compression chamber group C2 through a back pressure passage (not shown), receive pressure from the first compression chamber group C1 and the second compression chamber group C2 and establish a back pressure therein so as to maintain the fixed scroll 130 and the movable scroll 120 against each other during compression of gas by the scroll assembly 110 without being disengaged from each other by the pressure in the first compression chamber group C1 and the second compression chamber group C2.

The above description provides multiple independent discharge paths by improving the design of the compression chambers of the scroll assembly 110, while arranging the

respective discharge ports

143, 144 and modifying the head space of the compressor 100. Next, the design of the compression chamber group of the double-lap scroll assembly 110 will be described in detail.

In accordance with the principles of the present disclosure, the first compression pocket set C1 and the second compression pocket set C2 of the scroll assembly 110 may be designed to have the same capacity, which is a relatively simple design. Herein, the "capacity" of the compression chamber group means the volume or mass of the fluid sucked into the compression chamber group when the outermost low pressure chamber of each compression chamber group is just closed. The first compression pocket set C1 and the second compression pocket set C2 may also be designed to have different capacities if a better fit of the compressor 100 to the

downstream condensers

210, 220 is desired. This can be achieved by changing the profile design of the scroll blades of the non-orbiting scroll 120 and the orbiting scroll 130. It should be noted that the

downstream condensers

210, 220 connected to the compressor 100 may have different rated operating pressures to provide different temperatures of the working fluid, regardless of whether the capacities of the first compression pocket set C1 and the second compression pocket set C2 are the same.

If it is required to design the first and second compression chamber groups C1 and C2 to have different capacities, it can be achieved by designing the two

scroll blades

131, 132 and 121, 122 of the non-orbiting scroll 130 and the orbiting scroll 120 of the double scroll assembly 110 to have different line lengths or different line heights, respectively. For example, in one embodiment, the profile height of the first orbiting scroll blade 121 may be designed to be greater than the profile height of the second orbiting scroll blade 122, as shown in fig. 7. In another embodiment, the profile length of the first orbiting scroll blade 121 may be designed to be greater than the profile length of the second orbiting scroll blade 122, as shown in fig. 8. Thereby, a first compression chamber group C1 of a large capacity and a second compression chamber group C2 of a small capacity, or vice versa, may be provided. It should be noted that the first and second

non-orbiting scroll blades

131 and 132 of the non-orbiting scroll 130 are designed in a corresponding manner to the orbiting scroll 120, and a schematic view of the non-orbiting scroll 130 having such a design is shown in fig. 9 and 10, in which the non-orbiting scroll 130 having the first non-orbiting scroll blade 131 with a height greater than that of the second non-orbiting scroll blade 132 is shown in fig. 9, and the non-orbiting scroll 130 having the first non-orbiting scroll blade 131 with a length greater than that of the second non-orbiting scroll blade 132 is shown in fig. 10. Based on this embodiment, a variety of possible pressure outputs of the scroll assembly 110 are enabled by different profile designs and placement of the corresponding modulation passages.

Further, if the scroll assembly 110 does not have additional capacity modulation passages, in a preferred embodiment, the compression ratio of at least one of the two compression pocket sets C1, C2 may be designed to be equal to the system pressure ratio of the compressor heat pump system 10 to achieve a more energy efficient heat pump system. The pressure ratio of the compressor 100 is generally determined by the ratio of the discharge pressure of the compressor 100 to the intake pressure, and the system pressure ratio of the compressor heat pump system 10 is generally the ratio of the condenser working pressure (condensing pressure) to the evaporator working pressure (evaporating pressure). Generally, the heat pump system 10 is considered to be most efficient if the pressure ratio of the compressor 100 and the ratio between the condenser and evaporator pressures are the same; otherwise, there are instances of under-compression or over-compression, resulting in a decrease in the efficiency of the heat pump system 10. Therefore, by designing the compressor theoretical pressure ratio to be equal to the actual operating pressure ratio of the compressor heat pump system, an optimized system energy efficiency can be achieved. In the case where the suction pressure of the compressor 100 is determined, a desired discharge pressure may be obtained by designing the profile length and height of the scroll blades of the orbiting and

non-orbiting scrolls

120 and 130, that is, the profile length and height of the scroll blades are designed such that the ratio of the discharge pressure to the suction pressure corresponds to the system pressure ratio of the heat pump system 10.

Implementations of a scroll assembly 110, a compressor 100 having such a scroll assembly 110, and a heat pump system 10 including such a compressor 100 according to the present disclosure are substantially as described above. In accordance with the principles of the present disclosure, by varying the configuration of the compression pocket sets of the scroll assembly and the arrangement of the discharge ports, two (or even more) independent discharge paths are allowed to be provided from the scroll assembly, thereby enabling the supply of two (or even more) condensers downstream to provide two (or even more) working fluids of different temperatures. Based on this design principle, the structure of the compressor is also modified accordingly, and the head space of the compressor is modified accordingly in order to fit the individual discharge ports to achieve the desired plurality of discharge paths. The present disclosure provides an independent exhaust path, primarily by improving the structure of the compressor 100 itself, which not only helps to simplify the construction of the heat pump system 10, but also reduces the cost of the overall heat pump system 10.

Although various embodiments of the present invention have been described in detail herein, it is to be understood that this invention is not limited to the particular embodiments described and illustrated in detail herein, and that other modifications and variations may be effected by one skilled in the art without departing from the spirit and scope of the invention. All such variations and modifications are intended to be within the scope of the present invention. Moreover, all the components described herein can be replaced by other technically equivalent components.

Claims

1. A compressor heat pump system (10), comprising:

a compressor (100), the compressor (100) having two discharge paths independent of each other provided by a scroll assembly (110) of the compressor (100);

two condensers (210, 220) arranged downstream of the compressor and connected to the two discharge paths of the compressor, respectively;

an evaporator (200) arranged downstream of the condensers and connected to both condensers;

wherein the scroll assembly (110) comprises a non-orbiting scroll (130) and an orbiting scroll (120) cooperating with each other to compress a working fluid, the non-orbiting scroll comprising a first non-orbiting scroll blade (131) and a second non-orbiting scroll blade (132), the orbiting scroll comprising a first orbiting scroll blade (121) and a second orbiting scroll blade (122), the non-orbiting scroll and the orbiting scroll cooperating to define a first compression chamber group (C1) and a second compression chamber group (C2) independent of each other;

wherein the scroll assembly is provided with two discharge ports (143, 144) respectively communicating with the first and second compression chamber groups to provide two discharge paths; and is

Wherein at least one of the first compression pocket set and the second compression pocket set provides a pressure ratio equal to a system pressure ratio of the compressor heat pump system.

2. The compressor heat pump system (10) of claim 1 wherein two of said discharge ports are formed on an end plate of said non-orbiting or orbiting scroll (133; 123).

3. The compressor heat pump system (10) of claim 2 wherein both of said discharge ports are in direct communication with a first discharge port (O1) of said first compression pocket set and a second discharge port (O2) of said second compression pocket set, respectively.

4. The compressor heat pump system (10) of claim 1 wherein two of said discharge ports are formed in an additional cover plate (140) located in an upper portion of said scroll assembly (110).

5. The compressor heat pump system (10) of claim 4 wherein two discharge chambers (135, 136) are formed in the end plate of the non-orbiting scroll below the two discharge ports, the two discharge ports communicating with the first discharge port of the first compression pocket set and the second discharge port of the second compression pocket set via the two discharge chambers, respectively.

6. The compressor heat pump system (10) of claim 5 wherein said end plate of said non-orbiting scroll further has a modulation passage (137a-C, 138a-C) formed therein below said discharge plenum, said modulation passage opening into one or more compression pockets (C1A, C1B; C2A, C2B) of said first and/or second set of compression pockets and its opening in said discharge plenum being covered by a check valve (V).

7. The compressor heat pump system (10) of claim 1 wherein each of the two discharge ports (143, 144) extends to a housing of the compressor (100) and has an opening to the exterior formed on the housing of the compressor.

8. The compressor heat pump system (10) of claim 1 wherein a head space of the compressor is divided into two discharge chambers independent of each other, the two discharge ports each opening into a respective discharge chamber.

9. The compressor heat pump system (10) of claim 8 wherein an exterior of each discharge chamber is provided with a discharge connection for connecting to the condenser.

10. The compressor heat pump system (10) of any of claims 1-9 wherein the first compression pocket set and the second compression pocket set have the same capacity.

11. The compressor heat pump system (10) of any of claims 1-9 wherein the first compression pocket set and the second compression pocket set have different capacities.

12. The compressor heat pump system (10) of claim 11 wherein a profile of said first orbiting scroll blade (121) is greater than a profile of said second orbiting scroll blade (122) or a profile of said first orbiting scroll blade is greater than a profile of said second orbiting scroll blade.

13. The compressor heat pump system (10) of any one of claims 1 to 9 wherein the condensers have different nominal operating pressures.

14. A scroll assembly (110), the scroll assembly (110) comprising an orbiting scroll (120) and a non-orbiting scroll (130) cooperating with each other to compress a working fluid,

wherein the non-orbiting scroll comprises a first non-orbiting scroll blade (131) and a second non-orbiting scroll blade (132), the orbiting scroll comprises a first orbiting scroll blade (121) and a second orbiting scroll blade (122), and the non-orbiting scroll and the orbiting scroll cooperate to define a first compression chamber group (C1) and a second compression chamber group (C2) which are independent of each other;

wherein the scroll assembly is provided with two discharge ports (143, 144) respectively communicating with the first and second compression chamber groups to provide two discharge paths.

15. The scroll assembly (110) of claim 14, wherein two said exhaust ports are formed on an end plate (133; 123) of said non-orbiting or orbiting scroll.

16. The scroll assembly (110) according to claim 15, wherein two said discharge ports are in direct communication with a first discharge port (O1) of said first compression pocket set and a second discharge port (O2) of said second compression pocket set, respectively.

17. The scroll assembly (110) according to claim 14, wherein two of said discharge ports are formed on an additional cover plate (140) located at an upper portion of said scroll assembly.

18. The scroll assembly (110) as set forth in claim 17, wherein said cover plate includes two discharge chambers (135, 136) located below two of said discharge ports, said two discharge ports communicating with a first discharge port of said first compression pocket set and a second discharge port of said second compression pocket set via said two discharge chambers, respectively.

19. The scroll assembly (110) according to claim 18, wherein said end plate of said non-orbiting or orbiting scroll has a modulation passage (137a-C, 138a-C) formed therein communicating two said discharge ports with said first and second groups of compression chambers, said modulation passage opening into one or more compression chambers (C1A, C1B; C2A, C2B) of said first and/or second groups of compression chambers and its opening in said discharge chamber being covered by a one-way valve (V).

20. The scroll assembly (110) according to any one of claims 14 to 19, wherein said first compression pocket set and said second compression pocket set have the same volume.

21. The scroll assembly (110) according to any one of claims 14 to 19, wherein said first and second compression chamber sets have different capacities.

22. The scroll assembly (110) of claim 21, wherein the profile length of the first orbiting scroll blade (121) is greater than the profile length of the second orbiting scroll blade (122) or the profile height of the first orbiting scroll blade is greater than the profile height of the second orbiting scroll blade.

23. A scroll compressor (100) comprising a scroll assembly (110) according to any one of claims 14 to 22.