Refrigerant refrigeration cycle device, thermal management system and vehicle

Abstract

According to the refrigerant refrigeration circulating device, the heat management system and the vehicle, the space size of the refrigerant refrigeration circulating device is reduced by changing the structure of the refrigerant refrigeration circulating device, the internal volume of a system loop is reduced, and the refrigerant filling amount is reduced. The refrigerant refrigeration cycle device comprises a compressor shell with an inner cavity and a condensation and evaporation module, the condensation and evaporation module is integrated with a condenser and an evaporator, and the condensation and evaporation module is fixedly connected to the compressor shell in the radial direction of the inner cavity. The condenser and the compressor shell are integrated, so that the space size of the refrigerant refrigeration circulating device is reduced, the internal volume of a system loop is reduced, and the refrigerant filling amount is reduced.

Description

TECHNICAL FIELD

[0001] The utility model relates to the thermal management technical field of vehicle, specifically, relate to refrigerant refrigeration cycle device, thermal management system and vehicle. BACKGROUND

[0002] In modern automobile manufacturing industry, along with the increasing of consumer's comfort requirement to vehicle, the performance and efficiency of automobile air conditioning system as the key part of improving the driving experience become the focus of automobile manufacturers. Refrigerant refrigeration circuit as the core component of automobile air conditioning system, usually by compressor, condenser, evaporator and throttle valve these four main parts constitute. These parts in the traditional solution, usually as independent assembly installation, and through the complex air conditioning pipeline system is connected to each other, to realize the circulation flow and heat exchange of refrigerant.

[0003] However, the independent installation of four main parts leads to the increase of the space volume of refrigerant refrigeration cycle device, increases the occupation of whole vehicle space. Due to the increase of system circuit internal volume, in order to meet the refrigeration demand, must increase the refrigerant charge. UTILITY MODEL CONTENTS

[0004] The utility model aims at providing refrigerant refrigeration cycle device, thermal management system and vehicle, through the change of the structure of refrigerant refrigeration cycle device reduces the space volume of refrigerant refrigeration cycle device, reduces system circuit internal volume and reduces refrigerant charge.

[0005] To solve the above technical problem, the utility model provides a refrigerant refrigeration cycle device, refrigerant refrigeration cycle device includes the compressor casing with inner chamber and condensation and evaporation module, the condensation and evaporation module is integrated with condenser and evaporator, the condensation and evaporation module is fixedly connected along the radial direction of the inner chamber in the compressor casing.

[0006] By integrating condenser and compressor casing, the space volume of refrigerant refrigeration cycle device is reduced, the system circuit internal volume is reduced and the refrigerant charge is reduced.

[0007] Optionally, the condensation and evaporation module includes sealing plate, condensing shell and evaporation shell;

[0008] The sealing plate has oppositely arranged first plate wall and second plate wall, the first plate wall is radially abutted with the compressor casing, and the condensing shell and the evaporation shell are fixedly connected to the second plate wall.

[0009] Optionally, the compressor casing surrounds the inner chamber, and the inner chamber has a gas outlet and a gas inlet;

[0010] The condensing shell and the evaporating shell are distributed along an axial direction, the condensing shell is connected with the gas outlet, and the evaporating shell is connected with the gas inlet.

[0011] Optionally, the compressor shell is configured with a first refrigerant flow channel and a second refrigerant flow channel, at least part of the first refrigerant flow channel connects the gas outlet with the condenser, and at least part of the second refrigerant flow channel connects the gas inlet with the evaporator.

[0012] The second refrigerant flow channel and at least part of the first refrigerant flow channel are located between the inner cavity and the condensing and evaporating module in a radial direction.

[0013] Optionally, the first refrigerant flow channel comprises a first refrigerant sub-flow channel, the gas outlet is connected with the condensing inlet of the condenser through the first refrigerant sub-flow channel, the compressor shell is provided with a first flow channel pipe, the first flow channel pipe defines the first refrigerant sub-flow channel, and the first flow channel pipe and the compressor shell are in an integral molding structure.

[0014] Optionally, the compressor shell comprises a high-pressure shell segment, the high-pressure shell segment comprises a first connecting plate, part of the first connecting plate protrudes axially forward to form a first protruding part, the first connecting plate is in radial abutment with part of the side wall of the condensing and evaporating module, the first protruding part is provided with the gas outlet, and the first flow channel pipe is arranged on the first connecting plate.

[0015] Optionally, the first flow channel pipe is arranged on an end surface of the compressor shell in an axial direction, the first flow channel pipe has a gas outlet, the condensing inlet is connected with the gas outlet, and the gas outlet is arranged on a surface of the first connecting plate that abuts against the condensing and evaporating module.

[0016] Optionally, the first flow channel pipe further has a second port, and the second port is provided with a first sensor.

[0017] Optionally, the first flow channel pipe has a first pipe segment and a second pipe segment, the first pipe segment and the second pipe segment are arranged at an angle, and the second port is arranged at a position where the first pipe segment and the second pipe segment meet.

[0018] Optionally, the compressor shell further comprises a scroll shell segment connected with the high-pressure shell segment, part of a surface of the scroll shell segment is in radial abutment with the condensing and evaporating module.

[0019] The scroll shell segment is configured with a second refrigerant sub-flow channel, the second refrigerant sub-flow channel has a third port, the third port is connected with a condensing outlet of the condenser, and the third port is located on a surface of the scroll shell segment that is in radial abutment with the condensing and evaporating module.

[0020] Optionally, the condensing shell is projected in a direction perpendicular to the sealing plate to form a first projection on the sealing plate, the first projection being quadrilateral;

[0021] The condensing inlet and the condensing outlet are disposed along diagonals of the first projection.

[0022] Optionally, the evaporator further comprises an evaporating inlet and an evaporating outlet, the evaporating inlet being in communication with the condensing outlet through part of the second refrigerant flow channel, and the evaporating outlet being in communication with the air inlet through part of the second refrigerant flow channel.

[0023] The evaporating shell is projected in a direction perpendicular to the sealing plate to form a second projection on the sealing plate, the second projection being quadrilateral;

[0024] The condensing inlet and the condensing outlet are located on the same side of the second projection in the height direction.

[0025] A heat management system comprises a refrigerant refrigeration cycle device.

[0026] A vehicle comprises a heat management system. BRIEF DESCRIPTION OF DRAWINGS

[0027] The accompanying drawings incorporated in and forming a part of the specification illustrate embodiments of the present specification and, together with the description, serve to explain the principles of the present specification.

[0028] Figure 1 is a structural schematic view of the refrigerant refrigeration cycle device in the embodiments of the present utility model;

[0029] Figure 2 is an exploded schematic view of Figure 1 ;

[0030] Figure 3 is a sectional view of Figure 1 ;

[0031] Figure 4 is a radial side view of Figure 1 ;

[0032] Figure 5 is a structural schematic view of a heat exchange assembly;

[0033] Figure 6 is a structural schematic view of the heat exchange assembly after being connected with a high-pressure shell segment, showing a first refrigerant sub-flow channel;

[0034] Figure 7 is an axial side view of the front side of a moving scroll shell;

[0035] Figure 8 is an axial side view of the rear side of the moving scroll shell;

[0036] Figure 9 is Figure 1 part structure explosion schematic view, mainly shows low pressure shell segment and dynamic scroll casing;

[0037] Figure 10 is low pressure shell segment axial rear side shaft side view;

[0038] Figure 11 is low pressure shell segment axial front side shaft side view;

[0039] Figure 12 is low pressure shell segment radial side side view;

[0040] Figure 13 is low pressure shell segment and cover plate explosion schematic view;

[0041] Figure 14 is Figure 13 low pressure shell segment and cover plate combination structure schematic view;

[0042] Figure 15 is low pressure shell segment flow channel schematic view;

[0043] Figure 16 is fourth groove and fifth groove flow direction schematic view, one;

[0044] Figure 17 is fourth groove and fifth groove flow direction schematic view, two;

[0045] Figure 18 is fourth groove and fifth groove flow direction schematic view, three;

[0046] Figure 19 The flow channel connection schematic diagram of the refrigerant refrigeration circulating device in the embodiment of the utility model.

[0047] Wherein, Figures 1-19 The reference signs in the above are as follows:

[0048] 1 - compressor housing; 1a - inner cavity; 1a-1 - high pressure side; 1a-2 - low pressure side; 11 - high pressure shell section; 11a - first connecting plate; 11a-1 - plate outer wall; 11b - first flow channel pipe; 11b-1 - first pipe section; 11b-1a - gas outlet; 11b-1b - second outlet; 11b-2 - second pipe section; 11b-3 - first refrigerant sub-flow channel; 11c - first protrusion; 12 - scroll shell section; 121 - static scroll shell; 121a - static shell rear end face; 122 - dynamic scroll shell; 122a - dynamic scroll pipe section; 122b - second protrusion; 122b-1 - first groove; 122b-1a - fourth outlet; 122b-1b - third outlet; 122b-1c - second refrigerant sub-flow channel; 122c - dynamic shell rear end face; 122d - dynamic shell front end face; 122e - heat insulation cavity; 13 - low pressure shell section; 131 - low pressure front end face; 132 - low pressure rear end face; 133 - low pressure pipe shell; 134 - heat exchange plate part; 134a - first sub-part; 134a-1 - sub-part outer wall; 134a-2 - first area; 134a-3 - valve passage; 134a-3a - ninth outlet; 134a-3b - tenth outlet; 134a-4 - second groove; 134a-4a - fifth outlet; 134a-4b - sixth outlet; 134a-4c - third refrigerant sub-flow channel; 134a-5 - third groove; 134a-5a - seventh outlet; 134a-5b - gas inlet; 134a-5c - fourth refrigerant sub-flow channel; 134a-5d - eleventh outlet; 134b - second sub-part; 134b-1 - liquid storage cavity; 134b-1a - concave cavity; 135 - cover plate; 135a - one hole; 135b - two holes;

[0049] 2 - heat exchange assembly; 21 - condenser; 21a - condenser shell; 22 - evaporator; 22a - evaporator shell; 23 - sealing plate; 231 - first plate wall; 231a - condensing inlet; 231b - condensing outlet; 231c - evaporating outlet; 231d - evaporating inlet; 232 - second plate wall;

[0050] 3 - throttle valve;

[0051] 41 - first sealing structure; 42 - second sealing structure; 43 - third sealing structure;

[0052] 51 - first connecting assembly; 51a - first connecting piece; 52 - second connecting assembly; 52a - second connecting piece;

[0053] 61 - first sensor; 62 - second sensor. DETAILED DESCRIPTION

[0054] The above merely is the preferred embodiment of the present application, it should be pointed out that, for the ordinary skilled in the art, without departing from the principles of the present application, can make several improvements and refinements, these improvements and refinements should also be considered as the protection scope of the present application. In order for those skilled in the art to better understand the technical solutions of the present application, the present application is further described in detail below in conjunction with the drawings and specific embodiments.

[0055] As Figures 1-19 , Figure 1 is the structure schematic view of the refrigerant refrigeration cycle device in the embodiment of the present application; Figure 2 is Figure 1 the explosion schematic view; Figure 3 is Figure 1 the sectional view; Figure 4 is Figure 1 the radial side view; Figure 5 is the structure schematic view of the heat exchange assembly; Figure 6 is the structure schematic view of the heat exchange assembly after being connected with the high-pressure shell segment, and the first refrigerant sub-flow channel is shown; Figure 7 is the shaft side view of the front side of the moving scroll shell in the axial direction; Figure 8 is the shaft side view of the rear side of the moving scroll shell in the axial direction; Figure 9 is Figure 1 the partial structure explosion schematic view of the low-pressure shell segment and the moving scroll shell; Figure 10 is the shaft side view of the rear side of the low-pressure shell segment in the axial direction; Figure 11 is the shaft side view of the front side of the low-pressure shell segment in the axial direction; Figure 12 is the side view of the radial side of the low-pressure shell segment; Figure 13 is the explosion schematic view of the low-pressure shell segment and the cover plate; Figure 14 is Figure 13 the structure schematic view of the low-pressure shell segment and the cover plate after being combined; Figure 15 is the flow channel schematic view of the low-pressure shell segment; Figure 16 is the flow direction schematic view of the fourth groove body and the fifth groove body, one; Figure 17 is the flow direction schematic view of the fourth groove body and the fifth groove body, two; Figure 18 is the flow direction schematic view of the fourth groove body and the fifth groove body, three; Figure 19 The flow channel connection schematic view of the refrigerant refrigeration cycle device in the embodiment of the present application.

[0056] As Figure 1 , Figure 3 , Figure 6 , Figure 7 , Figure 15 and Figure 19As shown, the present application provides a refrigerant refrigeration cycle device, which comprises a heat exchange assembly 2 and a compressor housing 1 with an inner cavity 1a, the heat exchange assembly 2 comprises a condenser 21 and an evaporator 22, the compressor housing 1 encloses the inner cavity 1a, the inner cavity 1a is used to accommodate the moving vane and the static vane of the compressor to form a low-pressure side 1a-2 and a high-pressure side 1a-1, the low-pressure side 1a-2 is located on the side of the moving vane away from the static vane, and the high-pressure side 1a-1 is located on the side of the static vane away from the moving vane. Before the gas is compressed, the low-pressure gas enters the inner cavity 1a from the low-pressure side 1a-2, and as the moving vane moves, the gas is gradually compressed and pushed to the high-pressure side 1a-1.

[0057] The inner cavity 1a has a nearly cylindrical structure, the low-pressure side 1a-2 and the high-pressure side 1a-1 are arranged opposite along the axial direction of the inner cavity 1a, and the moving vane and the static vane are sequentially distributed along the axial direction of the inner cavity 1a. Specifically, the inner cavity 1a has a gas outlet 11b-1a and a gas inlet 134a-5b, the gas outlet 11b-1a is communicated with the high-pressure side 1a-1, and the gas inlet 134a-5b is communicated with the low-pressure side.

[0058] Please understand Figure 2 and Figures 11-14 In the present embodiment, the compressor housing 1 is integrated with a liquid storage cavity 134b-1 spaced from the inner cavity 1a, the liquid storage cavity 134b-1 is used to store high-pressure cooling liquid discharged from the condenser 21, and the part of the cooling liquid is stored in the liquid storage cavity 134b-1 after being converted from gaseous state to liquid state or gaseous-liquid mixed state by the condenser 21. In the conventional technical solution, the liquid storage cavity 134b-1 and the compressor housing 1 are separate structures, and the two are communicated through a pipeline, but such a way will cause the overall volume of the refrigerant refrigeration cycle device to increase. In the present embodiment, by integrating the liquid storage cavity 134b-1 in the compressor housing 1, the volume of the refrigerant refrigeration cycle device can be significantly reduced, and the integration degree of the refrigerant refrigeration cycle device can be improved.

[0059] In the present embodiment, the conventional external pipeline scheme is also changed, and the structure of the compressor housing 1 itself integrating the pipeline is adopted to further reduce the volume and liquid charging amount of the refrigerant refrigeration cycle device. Specifically, the compressor housing 1 is configured with a first refrigerant flow channel, the high-pressure side 1a-1 of the inner cavity 1a and the liquid storage cavity 134b-1 are communicated through the first refrigerant flow channel, and the condenser 21 is arranged between the high-pressure side 1a-1 and the liquid storage cavity 134b-1.

[0060] Specifically, the first refrigerant flow channel includes a first refrigerant sub-flow channel 11b-3 and a second refrigerant sub-flow channel 122b-1c, the high-pressure side 1a-1 is connected to the condensing inlet 231a of the condenser 21 through the first refrigerant sub-flow channel 11b-3, and the condensing outlet 231b of the condenser 21 is connected to the liquid storage cavity 134b-1 through the second refrigerant sub-flow channel 122b-1c. The high-temperature gaseous refrigerant from the high-pressure side 1a-1 enters the condenser 21 through the first refrigerant sub-flow channel 11b-3 and the condensing inlet 231a and exchanges heat in the condenser 21. The heat exchange medium circulating in the condenser 21 can be an ethylene glycol aqueous solution or other heat exchange medium. The improvement of the present application is not focused on the specific structure of the condenser 21, which will not be described here.

[0061] The compressor housing 1 is also configured with a second refrigerant flow channel, the liquid storage cavity 134b-1 is connected to the low-pressure side 1a-2 through the second refrigerant flow channel, and the second refrigerant flow channel is connected to the throttling valve 3 and the evaporator 22. In the flow direction of the refrigerant, the position of the throttling valve 3 connected to the second refrigerant flow channel is located upstream of the connection position of the evaporator 22.

[0062] The second refrigerant flow channel includes an upstream medium-temperature flow section and a downstream low-temperature flow section. The part of the second refrigerant flow channel between the outlet of the liquid storage cavity 134b-1 and the inlet of the evaporator 22 is defined as the upstream medium-temperature flow section, and the part of the second refrigerant flow channel between the outlet of the evaporator 22 and the low-pressure side 1a-2 is defined as the downstream low-temperature flow section. The throttling valve 3 is arranged in the upstream medium-temperature flow section.

[0063] The compressor housing 1 includes a heat exchange plate part 134, the third refrigerant sub-flow channel 134a-4c and the fourth refrigerant sub-flow channel 134a-5c are arranged in the heat exchange plate part 134, and the heat exchange plate part 134 is made of a material capable of rapid heat conduction such as metal. The liquid storage cavity 134b-1 is connected to the evaporating inlet 231d through the third refrigerant sub-flow channel 134a-4c, the evaporating outlet 231c is connected to the low-pressure side 1a-2 through the fourth refrigerant sub-flow channel 134a-5c, and the refrigerant in the third refrigerant sub-flow channel 134a-4c can exchange heat with the refrigerant in the fourth refrigerant sub-flow channel 134a-5c.

[0064] Therefore, in the technical solution of the present application, the refrigerant in the upstream medium-temperature flow section and the fourth refrigerant sub-flow channel 134a-5c can exchange heat through the heat exchange plate part 134 during circulation, further improving the cooling efficiency of the refrigerant.

[0065] In actual operation, the medium-temperature, high-pressure liquid refrigerant from the storage chamber 134b-1 has a relatively high temperature. This portion of the medium-temperature, high-pressure liquid refrigerant passes through the upstream medium-temperature flow section, successively through the throttling valve 3 and the evaporation inlet 231d, and then enters the evaporator 22 for further cooling and depressurization, thus forming a low-pressure, low-temperature gaseous refrigerant. Specifically, the medium-temperature, high-pressure liquid refrigerant from the upstream medium-temperature flow section is transformed into a low-temperature, low-pressure liquid refrigerant after passing through the throttling valve 3, and then enters the evaporator for evaporation and phase change, becoming a low-temperature, low-pressure gaseous refrigerant. The low-temperature, low-pressure gaseous refrigerant flows back to the low-pressure side 1a-2 of the inner cavity 1a after passing through the fourth refrigerant sub-channel 134a-5c. During the refrigerant flow, the low-pressure, low-temperature gaseous refrigerant flowing through the fourth refrigerant sub-channel 134a-5c can also exchange heat with the medium-temperature, high-pressure liquid refrigerant flowing in the upstream medium-temperature section. After heat exchange, the temperature of the medium-temperature, high-pressure liquid refrigerant is further reduced, increasing its subcooling. The increase in subcooling can improve the efficiency of the throttling valve. This improves the efficiency of the entire compression refrigeration cycle while ensuring that the refrigerant entering the compressor is gaseous, which can reduce the compressor's compression power to a certain extent.

[0066] like Figures 4 to 6 The content shown and combined Figure 7 and Figure 9 In some embodiments of this application, the condenser 21 and the evaporator 22 are integrated into a complete module, and the heat exchange assembly 2 is fixedly connected to one side of the compressor housing 1 along the radial direction of the inner cavity 1a.

[0067] Specifically, the heat exchange assembly 2 includes a sealing plate 23, a condenser shell 21a, and an evaporator shell 22a. The condenser shell 21a houses the components of the condenser 21, and the evaporator shell 22a houses the components of the evaporator 22. The sealing plate 23 has a first plate wall 231 and a second plate wall 232 that are radially opposite each other. The first plate wall 231 abuts radially against the compressor housing 1, and both the condenser shell 21a and the evaporator shell 22a are fixedly connected to the second plate wall 232.

[0068] In the example shown, the condenser 21 and evaporator 22 are sequentially distributed along the axial direction of the inner cavity 1a. The condenser 21 is closer to the high-pressure side 1a-1 than the evaporator 22, and the evaporator 22 is closer to the low-pressure side 1a-2 than the condenser 21. That is, the condenser shell 21a and the evaporator shell 22a are distributed along the axial direction, with the condenser shell 21a closer to the high-pressure side 1a-1 and the evaporator shell 22a closer to the low-pressure side 1a-2, which further simplifies the flow channel length.

[0069] In this embodiment, the portion of the compressor housing 1 with the first refrigerant flow channel and the second refrigerant flow channel is located between the portion of the compressor housing 1 with the inner cavity 1a and the heat exchange component 2, thereby further improving the space utilization of the refrigerant refrigeration cycle device.

[0070] In order to improve the overall strength of the refrigerant refrigeration cycle device, the first plate wall 231 is a straight wall, and the part of the compressor shell 1 radially abutting against the first plate wall 231 is in contact with the first plate wall 231. In this way, the compressor shell 1 and the sealing plate 23 are in radial surface contact and abut, thereby ensuring the relative position of the compressor shell 1 and the sealing plate 23 in the radial direction.

[0071] The structure of the compressor shell 1 in the present application will be described in detail below.

[0072] As shown in Figure 2 , Figure 3 and Figure 4 , the compressor shell 1 in the present application includes a high-pressure shell section 11, a scroll shell section 12 for accommodating the aforementioned moving scroll and stationary scroll, and a low-pressure shell section 13 defining a low-pressure side 1a-2 of the inner cavity 1a. The high-pressure shell section 11 defines a high-pressure side 1a-1 of the inner cavity 1a, and the high-pressure shell section 11, the scroll shell section 12, and the low-pressure shell section 13 are sealingly and fixedly connected.

[0073] In the example as shown in the figure, the high-pressure shell section 11 includes a first connecting plate 11a, and a first flow channel pipe 11b. The first connecting plate 11a is axially protruded in front to form a first protruding portion 11c. "Front" refers to the side farther away from the center of the inner cavity 1a in the axial direction, and vice versa. In the present application, front and back can be understood in the direction shown in the figure. The inner wall of the first protruding portion 11c encloses a part of the inner cavity 1a and serves as the high-pressure side 1a-1. The first flow channel pipe 11b is arranged on the axial end surface of the compressor shell 1, and has a gas outlet 11b-1a; the condensing inlet 231a is in opposite connection with the gas outlet 11b-1a. By arranging the first flow channel pipe 11b on the end surface of the inner cavity 1a, the first flow channel pipe 11b can be adapted to the position of the condensing inlet 231a, further reducing the length of the pipeline.

[0074] The first flow channel pipe 11b is arranged on the first connecting plate 11a; the first flow channel pipe 11b defines a first refrigerant sub-flow channel 11b-3, and the first flow channel pipe 11b, the first protruding portion 11c, and the first connecting plate 11a are integrally formed.

[0075] The first connecting plate 11a has a plate outer wall 11a-1, which is radially opposite to the inner cavity 1a and is located away from the inner cavity 1a. The plate outer wall 11a-1 is in radial abutment with part of the side wall of the heat exchange assembly 2.

[0076] As shown in the example, the first flow channel pipe 11b includes a first pipe segment 11b-1 and a second pipe segment 11b-2, the first pipe segment 11b-1 is arranged at an angle with the second pipe segment 11b-2. The first pipe segment 11b-1 extends radially and is arranged at the top end of the first connecting plate 11a in the height direction of the heat exchange assembly 2, and the second pipe segment 11b-2 is arranged perpendicular to the first pipe segment 11b-1, and the bottom end of the second pipe segment 11b-2 is communicated with the first protruding portion 11c. Of course, the first pipe segment 11b-1 and the second pipe segment 11b-2 can also be arranged at an acute angle or an obtuse angle, which can be arranged by those skilled in the art.

[0077] The outlet 11b-1a is located at the top end of the outer wall 11a-1 of the plate and radially faces the sealing plate 23, and is opposite to the inlet of the condenser 21 arranged on the sealing plate 23.

[0078] Of course, the first flow channel pipe 11b can also be arranged at the bottom of the first connecting plate 11a, that is, the outlet 11b-1a is located at the bottom of the first connecting plate 11a and radially faces the sealing plate 23, and the inlet of the condenser 21 is correspondingly arranged.

[0079] In combination Figure 6 In the axial direction, the first protruding portion 11c protrudes beyond the surface where the first connecting plate 11a is located, and the top end and the bottom end of the outer wall 11a-1 of the plate are respectively provided with bolt connection grooves which can be matched with the sealing plate 23, and the bolt connection grooves extend radially.

[0080] In the example shown in the figure, one bolt connection groove is located at the top side wall of the first flow channel pipe 11b, and the other bolt connection groove is located at the bottom of the first connecting plate 11a.

[0081] Therefore, by protruding the first protruding portion 11c beyond the surface where the first connecting plate 11a is located, and using the first connecting plate 11a to abut the heat exchange assembly 2 radially and form a bolt connection, the part of the high-pressure shell segment 11 connected with the sealing plate 23 can be moved inward in the axial direction, thereby providing more space for the arrangement of the first flow channel pipe 11b, and improving the utilization rate of the axial space of the refrigerant refrigeration circulating device.

[0082] As shown in the example, the first flow channel pipe 11b also has a second port 11b-1b, and the second port 11b-1b is provided with a first sensor 61. The first sensor 61 is a temperature and pressure sensor, and the compression efficiency of the compressor is adjusted according to the temperature and pressure values in the first flow channel pipe 11b collected by the first sensor 61.

[0083] Optionally, the first flow channel pipe 11b has a second port 11b-1b arranged at the position where the first pipe section 11b-1 and the second pipe section 11b-2 meet. Specifically, the second port 11b-1b is axially arranged at the side of the first flow channel pipe 11b opposite to the first protruding portion 11c. In this way, the original axial space can be further utilized, and the axial space utilization rate of the refrigerant refrigeration cycle device can be improved.

[0084] Recombination Figure 3 In some other embodiments, the compressor housing 1 includes a scroll housing section 12 fixedly connected with the high-pressure shell section 11, and the second refrigerant sub-flow channel 122b-1c is configured in the scroll housing section 12. In the axial direction, the scroll housing section 12 is closer to the low-pressure side la-2 than the high-pressure shell section 11, so that the temperature of the refrigerant flowing through the scroll housing section 12 is lower than the temperature of the refrigerant in the high-pressure shell section 11. The second refrigerant sub-flow channel 122b-1c communicates with the condensing outlet 231b, and the temperature of the refrigerant therein is lower than the temperature in the first refrigerant sub-flow channel 11b-3. By arranging the second refrigerant sub-flow channel 122b-1c in the scroll housing section 12, the refrigerant in the second refrigerant sub-flow channel 122b-1c can be further cooled, and the liquid fraction of the refrigerant entering the liquid storage cavity 134b-1 can be improved.

[0085] Combination Figure 4 , Figure 6 and Figure 7 The scroll housing section 12 includes an axially connected static scroll housing 121 and a dynamic scroll housing 122. The dynamic scroll housing 122 further includes a dynamic scroll pipe section 122a and a second protruding portion 122b fixedly connected with the dynamic scroll pipe section 122a. The dynamic scroll pipe section 122a defines a partial inner cavity la therein, and the second protruding portion 122b extends from the dynamic scroll pipe section 122a toward the side close to the heat exchange assembly 2 until the second protruding portion 122b radially abuts against the partial side wall of the heat exchange assembly 2.

[0086] The second protruding portion 122b is provided with at least a partial second refrigerant sub-flow channel 122b-1c. The second refrigerant sub-flow channel 122b-1c has a third port 122b-1b and a fourth port, both of which are located in the dynamic scroll housing 122. The third port 122b-1b is located at the portion where the second protruding portion 122b radially abuts against the heat exchange assembly 2, and is used to be connected with the condensing outlet 231b arranged on the cover plate 23.

[0087] In the case of Figure 4 , Figure 7 and Figure 8In the example shown, in the height direction, the third port 122b-1b is located on the lower side of the second protrusion 122b. In this way, on the side where the compressor housing 1 is located, the third port 122b-1b and the gas outlet 11b-1a are arranged on the upper and lower sides of the compressor housing 1 in the height direction. Correspondingly, the condenser inlet 231a and the condenser outlet 231b are arranged along the diagonal lines of the first projection formed on the cover plate 23.

[0088] The orbiting scroll case 122 includes an orbiting case front end surface 122d, and the fixed scroll case 121 further has a fixed case rear end surface 121a axially abutting the orbiting case front end surface 122d. Here, “front” and “rear” are defined with reference to the axial direction of the inner cavity 1a, with the direction pointing to the high-pressure side 1a-1 being defined as the front, and the opposite direction being defined as the rear.

[0089] Continuing with Figure 3 , Figure 4 and Figure 8 , the region of the orbiting case front end surface 122d corresponding to the second protrusion 122b is axially recessed to form a first groove 122b-1, the third port 122b-1b is in communication with the first groove 122b-1, the first groove 122b-1 is spaced apart from the inner cavity 1a, and the first groove 122b-1 and part of the fixed case rear end surface 121a enclose a second refrigerant sub-flow passage 122b-1c.

[0090] In the example shown, the first groove 122b-1 extends in the height direction, and at one end of the extension direction of the first groove 122b-1, the third port 122b-1b is connected, and at the other end, a fourth port is connected. The fourth port is in communication with the liquid storage cavity 134b-1. Specifically, the orbiting scroll case 122 further has an orbiting case rear end surface 122c axially opposite the orbiting case front end surface 122d, and the fourth port is located on the orbiting case rear end surface 122c.

[0091] That is, in the present embodiment, the second refrigerant sub-flow passage 122b-1c utilizes the axial and radial space of the second protrusion 122b, thereby integrating the second refrigerant sub-flow passage 122b-1c into the scroll case. In the above-described embodiment, the liquid storage cavity 134b-1 is located axially on the rear side of the second protrusion 122b, where the rear side refers to the direction axially pointing to the low-pressure side 1a-2. That is, the liquid storage cavity 134b-1 corresponds to the rear side of the scroll case segment 12 in the axial direction. In this way, the distribution of the flow passages can be further rationalized, and the size of the refrigerant refrigeration cycle device can be further reduced.

[0092] In the embodiments of the present application, a heat insulation cavity 122e is arranged between the radial moving scroll pipe section 122a and the second protruding section 122b. In this way, heat exchange between the refrigerant in the cavity and the refrigerant in the second refrigerant sub-flow channel 122b-1c can be avoided.

[0093] In the above embodiments, please refer to Figure 6 、 Figure 7 、 Figure 9 and Figure 14 , a first sealing structure 41 is arranged between the front end surface of the moving shell 122d and the rear end surface of the static shell 121a, part of the first sealing structure 41 is arranged around the inner cavity 1a, and part of the first sealing structure 41 is arranged around the first groove 122b-1. In the scheme in which the heat insulation cavity 122e is arranged, part of the first sealing structure 41 is also arranged around the heat insulation cavity 122e, so that the heat insulation cavity 122e, the inner cavity 1a, and part of the second refrigerant sub-flow channel 122b-1c can be sealed.

[0094] In the schemes of the present application, in addition to the above-mentioned embodiments, the first groove 122b-1 can also be located at the rear end surface of the mirror disc, or part of the first groove 122b-1 is located at the front end surface of the moving disc, and part of the first groove 122b-1 is located at the rear end surface of the static disc. The same or equivalent schemes also belong to the protection scope of the present patent.

[0095] In some other embodiments, the compressor shell 1 further comprises a low-pressure shell section 13 connected to the scroll shell section 12, in the axial direction, the low-pressure shell section 13 is connected to the side of the scroll shell section 12 away from the high-pressure shell section 11, and the low-pressure shell section 13 defines a low-pressure side 1a-2. In the present embodiment, the liquid storage cavity 134b-1 is integrated in the low-pressure shell section 13, so that the high-temperature and high-pressure liquid refrigerant in the liquid storage cavity 134b-1 can exchange heat with the medium sucked into the low-pressure shell section 13, thereby ensuring the gaseous state of the refrigerant sucked into the low-pressure shell section 13.

[0096] The low-pressure shell section 13 comprises a low-pressure pipe shell 133 and a third protruding section connected to the low-pressure pipe shell 133, the low-pressure pipe shell 133 surrounds and defines part of the inner cavity 1a, and the third protruding section is located at the same side as the second protruding section 122b, and the low-pressure shell section 13 protrudes radially outward until the surface of the third protruding section radially away from the low-pressure pipe shell 133 directly or indirectly abuts against the heat exchange assembly 2. In this way, the low-pressure shell section 13 also abuts against the sealing plate 23 in the radial direction, thereby ensuring the support of the compressor shell 1 to the heat exchange assembly 2.

[0097] In the scheme of the present application, the second refrigerant flow channel is arranged in the third protruding portion, that is, the third refrigerant sub-flow channel 134a-4c and the fourth refrigerant sub-flow channel 134a-5c are both arranged in the third protruding portion, and at least part of the liquid storage cavity 134b-1 is also arranged in the third protruding portion, the part of the third protruding portion where the second refrigerant flow channel is arranged is defined as a first sub-portion 134a, and the part of the third protruding portion where part of the liquid storage cavity 134b-1 is arranged is defined as a second sub-portion 134b; the first sub-portion 134a and the second sub-portion 134b are sequentially arranged along the axial direction, and in the axial direction, the first sub-portion 134a is located at the rear side of the second sub-portion 134b.

[0098] When the first sub-portion 134a, the second sub-portion 134b, and the inner cavity 1a are projected in the radial direction, the projection range of the first sub-portion 134a coincides with the projection range of the inner cavity 1a, and the projection range of the second sub-portion 134b also coincides with the projection range of the inner cavity 1a, and in the axial direction, the projection range of the first sub-portion 134a is adjacent to the projection range of the second sub-portion 134b. That is, in the present scheme, in the axial direction, the fourth refrigerant sub-flow channel 134a-5c is located on the side of the third refrigerant sub-flow channel 134a-4c away from the second sub-portion 134b.

[0099] Since the refrigerant in the third refrigerant sub-flow channel 134a-4c of the second refrigerant flow channel comes from the liquid storage cavity 134b-1, its temperature is relatively high, and when the medium flows along the third refrigerant sub-flow channel 134a-4c, it can also exchange heat with the refrigerant sucked into the low-pressure side 1a-2 to a certain extent.

[0100] Alternatively, in the axial direction, the fourth refrigerant sub-flow channel 134a-5c is located on the side of the third refrigerant sub-flow channel 134a-4c away from the liquid storage cavity 134b-1, thereby not only further reducing the length of the pipeline, but also enabling the third refrigerant sub-flow channel 134a-4c to exchange heat with the medium in the fourth refrigerant sub-flow channel 134a-5c while exchanging heat with the low-pressure side 1a-2 refrigerant.

[0101] In the present embodiment, the aforementioned heat exchange plate portion 134 belongs to the low-pressure shell segment 13, and specifically, the third protruding portion serves as the aforementioned heat exchange plate portion 134.

[0102] The specific structure of the liquid storage cavity 134b-1 will be described below.

[0103] In some specific embodiments, the low-pressure shell segment 13 has a low-pressure front end surface 131, and part of the low-pressure front end surface 131 is recessed in the axial direction towards the direction close to the low-pressure side 1a-2 to form a recessed cavity 134b-1a, that is, the low-pressure front end surface 131 is recessed in the axial direction to form the recessed cavity 134b-1a, and the recessed cavity 134b-1a has a certain depth in the axial direction, and the recessed cavity 134b-1a is located in the aforementioned second sub-portion 134b.

[0104] The orbiting scroll shell 122 of the scroll shell segment 12 has an orbiting shell rear end surface 122c which axially abuts the low-pressure front end surface 131, and part of the orbiting shell rear end surface 122c and the concave cavity 134b-1a jointly form the liquid storage cavity 134b-1. The fourth port mentioned above is located on the part of the orbiting shell rear end surface 122c which is located in the concave cavity 134b-1a. In the scheme of the present application, the concave cavity 134b-1a constitutes the entire containing space of the liquid storage cavity 134b-1, that is, the liquid storage cavity 134b-1 does not face the scroll shell segment 12, thereby avoiding heat exchange between the high-temperature and high-pressure liquid refrigerant in the liquid storage cavity 134b-1 and the refrigerant in the scroll shell segment 12.

[0105] The part of the third protruding portion and the part of the outer wall of the low-pressure tube shell 133 jointly form the concave cavity 134b-1a. That is, the part of the wall of the concave cavity 134b-1a is formed by the part of the outer wall of the low-pressure tube shell 133, that is, part of the wall of the concave cavity 134b-1a is shaped along the inner cavity 1a, thereby increasing the contact area between the liquid storage cavity 134b-1 and the inner cavity 1a.

[0106] The specific structure of the second refrigerant flow channel in the present application will be further described below with some specific embodiments.

[0107] The surface of the first sub-portion 134a facing the heat exchange assembly 2 is defined as a sub-portion outer wall 134a-1, and the sub-portion outer wall 134a-1 is provided with a second groove 134a-4 and a third groove 134a-5. The low-pressure shell segment 13 further comprises a cover plate 135 which is radially arranged on the sub-portion outer wall 134a-1.

[0108] The cover plate 135 is radially attached to the sub-portion outer wall 134a-1, the second groove 134a-4 and part of the cover plate 135 jointly form a part of the third refrigerant sub-flow channel 134a-4c, and the third groove 134a-5 and part of the cover plate 135 jointly form a part of the fourth refrigerant sub-flow channel 134a-5c.

[0109] Specifically, the second groove 134a-4 is provided with a fifth port 134a-4a and a sixth port 134a-4b, and the fifth port 134a-4a and the sixth port 134a-4b are located at the end of the corresponding side in the extension direction. The second groove 134a-4 is connected with the liquid storage cavity 134b-1 through the fifth port 134a-4a, that is, part of the third refrigerant sub-flow channel 134a-4c extends through the wall shared by the concave cavity 134b-1a and the second groove 134a-4 in the axial direction, and the fifth port 134a-4a is arranged on the second groove 134a-4, and this part of the flow channel penetrates the cavity wall of the concave cavity 134b-1a to form the corresponding port (not shown in the figure).

[0110] The second groove 134a-4 is communicated with the evaporation inlet 231d through the sixth port 134a-4b. The cover plate 135 is provided with a second hole 135b which is adapted to the sixth port 134a-4b and is adapted to the evaporation inlet 231d. The sixth port 134a-4b is communicated with the evaporation inlet 231d through the second hole 135b. The evaporation inlet 231d is also provided on the aforementioned sealing plate 23.

[0111] In the present embodiment, the third refrigerant sub-flow passage 134a-4 is further provided with a throttling valve 3. The first sub-portion 134a has a first region 134a-2 which is used to integrate the throttling valve 3. The first region 134a-2 radially extends beyond the low-pressure tube shell 133. The first region 134a-2 is provided with a valve channel 134a-3 which penetrates the first sub-portion 134a and forms a ninth port 134a-3a on the sub-portion outer wall 134a-1 and a tenth port 134a-3b on the sub-portion inner wall opposite to the sub-portion outer wall 134a-1. Part of the throttling valve 3 is inserted into the valve channel 134a-3 through the tenth port 134a-3b. The throttling valve 3 has a valve inlet and a valve outlet which are both located in the valve channel 134a-3.

[0112] The second groove 134a-4 is communicated with the valve inlet of the throttling valve 3 through the sixth port 134a-4b. The valve outlet of the throttling valve 3 is communicated with the evaporation inlet 231d through the ninth port 134a-3a.

[0113] In the present embodiment, please refer to Figure 3 、 Figure 4 、 Figure 6 、 Figure 7 and Figure 10 、 Figure 16 , the high-temperature and high-pressure liquid refrigerant from the liquid storage cavity 134b-1 enters the second groove 134a-4 through the fifth port 134a-4a and flows along the second groove 134a-4 to the sixth port 134a-4b, and enters the valve inlet of the throttling valve 3 through the sixth port 134a-4b, enters the valve cavity, and then enters the evaporator 22 through the valve outlet, the seventh port 134a-5a and the evaporation inlet 231d, so as to be cooled and decompressed.

[0114] The third groove 134a-5 has a seventh port 134a-5a and an inlet port 134a-5b, the seventh port 134a-5a is located at one end of the third groove 134a-5 in the extension direction of the third groove 134a-5, and the inlet port 134a-5b is located at the other end. The cover plate 135 is provided with a hole 135a matched with the seventh port 134a-5a, and the seventh port 134a-5a is connected with the evaporation outlet 231c through the hole. The inlet port 134a-5b is connected with the low-pressure side 1a-2. In the example shown in the figure, the seventh port 134a-5a is located at the top end of the third groove 134a-5, and the inlet port 134a-5b is located at the bottom end. In the height direction of the heat exchange assembly 2, the sixth port 134a-4b and the seventh port 134a-5a are located on the same side. Thus, the evaporation inlet 231d and the evaporation outlet 231c are arranged conveniently, and the fifth port 134a-4a arranged at the bottom can also achieve better communication of the liquid storage cavity 134b-1.

[0115] The low-pressure shell section 13 further comprises a low-pressure rear end surface 132; the part of the low-pressure rear end surface 132 located in the first sub-section 134a has an eleventh port 134a-5d, the eleventh port 134a-5d is connected with the third groove 134a-5 through the seventh port 134a-5a; the eleventh port 134a-5d is provided with a second sensor 62, which is also a temperature and pressure sensor to detect the temperature and pressure of the refrigerant entering the low-pressure side 1a-2.

[0116] The structure of the second groove 134a-4 and the third groove 134a-5 in the present application will be illustrated below with three specific examples. The same or equivalent solutions as the following examples also belong to the protection scope of the present application. The structure of the second groove 134a-4 and the structure of the third groove 134a-5 in the following different examples can be combined arbitrarily, and the combined solutions also belong to the protection scope of the present patent.

[0117] In one example, as shown in Figure 16 , the third groove 134a-5 extends linearly along the height direction of the heat exchange assembly 2, and the second groove 134a-4 extends spirally along the height direction of the heat exchange assembly 2.

[0118] In another example, as shown in Figure 17 , different from the previous example, the second groove 134a-4 extends spirally along the axial direction.

[0119] In a third example, as shown in Figure 18As shown, the third groove 134a-5 extends in a wave shape along the height direction of the heat exchange assembly 2. The second groove 134a-4 extends in a wave shape along the height direction of the heat exchange assembly 2. Optionally, at least part of the third groove 134a-5 and the second groove 134a-4 extend in a wave shape. In this way, the axial distance between the second groove 134a-4 and the third groove 134a-5 can be shortened.

[0120] By using these ways, the heat exchange rate between the second groove 134a-4, the third groove 134a-5, the inner cavity 1a and the liquid storage cavity 134b-1 can be increased.

[0121] In one specific example, the third refrigerant sub-flow path 134a-4c is high-pressure liquid refrigerant, and the temperature range is 50-70℃. The fourth refrigerant sub-flow path 134a-5c is low-pressure liquid refrigerant, and the temperature range is 0-10℃. In this way, heat exchange can occur between the third refrigerant sub-flow path 134a-4c and the fourth refrigerant sub-flow path 134a-5c.

[0122] In any of the foregoing embodiments, the refrigerant refrigeration cycle device includes a first connecting assembly 51 and a second connecting assembly 52. The first connecting assembly 51 includes a plurality of first connecting members 51a, and the second connecting assembly 52 includes a plurality of second connecting members 52a. Each of the connecting members includes a connecting rod and a locking device. The connecting rod extends in the axial direction, and the locking device is used to lock the connecting rod in the axial direction.

[0123] Specifically, the first connecting assembly 51 is used to axially fix and connect the high-pressure shell segment 11, the scroll shell segment 12 and the low-pressure shell segment 13. The plurality of first connecting members 51a are arranged around the inner cavity 1a. The second connecting assembly 52 is used to axially fix and connect the scroll shell segment 12 and the low-pressure shell segment 13. The plurality of second connecting members 52a and part of the first connecting members 51a are arranged around the liquid storage cavity 134b-1.

[0124] In some more specific ways, the refrigerant refrigeration cycle device further includes a second sealing structure 42 and a third sealing structure 43. The second sealing structure 42 is arranged on the end face of the static scroll shell 121 away from the dynamic scroll shell 122, i.e., between the static shell front end face and the first connecting plate 11a, and is arranged around the inner cavity 1a. Each of the first connecting members 51a passes through the outer side of the second sealing structure 42. In this way, the second sealing structure 42 can be limited during installation, and radial deviation of the second sealing structure 42 during use can be avoided.

[0125] The third sealing structure 43 is arranged between the low-pressure front end surface 131 and the moving shell rear end surface 122c, and a part of the third sealing structure 43 surrounds the inner cavity 1a, and a part of the third sealing structure 43 surrounds the recessed cavity 134b-1a. The first connecting member 51a passes through the part of the third sealing structure 43 surrounding the inner cavity 1a, and the second connecting member 52a passes through the part of the third sealing structure 43 surrounding the recessed cavity 134b-1a. The third sealing structure 43 is an integrally formed structure, thereby facilitating processing and installation.

[0126] Of course, the first connecting member 51a passes through the part of the first sealing structure 41 surrounding the inner cavity 1a, and the second connecting member 52a passes through the part of the first sealing structure 41 surrounding the first groove 122b-1.

[0127] In this way, the various sealing structures can be locked in the axial direction, thereby achieving the cooling sealing of the refrigerant refrigeration cycle device in the present application.

[0128] The above is only a preferred embodiment of the present application, and it should be pointed out that for ordinary skilled in the art, without departing from the principles of the present application, a number of improvements and refinements can be made, and these improvements and refinements should be considered as the protection scope of the present application.

Claims

1. A refrigerant refrigeration cycle device, characterized in that, The compressor housing (1) includes an inner cavity (1a) and a condenser-evaporator module (2), which integrates a condenser (21) and an evaporator (22). The condenser-evaporator module (2) is fixedly connected to the compressor housing (1) radially along the inner cavity (1a).

2. The refrigerant refrigeration cycle device according to claim 1, characterized in that, The condensation-evaporation module (2) includes a sealing plate (23), a condensation shell (21a), and an evaporation shell (22a); The sealing plate (23) has a first plate wall (231) and a second plate wall (232) arranged opposite to each other. The first plate wall (231) abuts radially against the compressor housing (1). The condenser shell (21a) and the evaporator shell (22a) are both fixedly connected to the second plate wall (232).

3. The refrigerant refrigeration cycle device according to claim 2, characterized in that, The compressor housing (1) forms an inner cavity (1a), which has an air outlet (11b-1a) and an air inlet (134a-5b). The condenser shell (21a) and the evaporator shell (22a) are distributed along the axial direction. The condenser shell (21a) is connected to the air outlet (11b-1a), and the evaporator shell (22a) is connected to the air inlet (134a-5b).

4. The refrigerant refrigeration cycle device according to claim 3, characterized in that, The compressor housing (1) is constructed with a first refrigerant channel and a second refrigerant channel. At least a portion of the first refrigerant channel connects the outlet (11b-1a) to the condenser (21), and at least a portion of the second refrigerant channel connects the inlet (134a-5b) to the evaporator (22). The second refrigerant channel and at least a portion of the first refrigerant channel are located radially between the inner cavity (1a) and the condensation and evaporation module (2).

5. The refrigerant refrigeration cycle device according to claim 4, characterized in that, The first refrigerant flow channel includes a first refrigerant sub-flow channel (11b-3), and the outlet (11b-1a) is connected to the condenser inlet (231a) of the condenser (21) through the first refrigerant sub-flow channel (11b-3); the compressor housing (1) is provided with a first flow channel pipe (11b), the first flow channel pipe (11b) defines the first refrigerant sub-flow channel (11b-3), and the first flow channel pipe (11b) and the compressor housing (1) are integrally formed.

6. The refrigerant refrigeration cycle device according to claim 5, characterized in that, The compressor housing (1) includes a high-pressure housing section (11), the high-pressure housing section (11) includes a first connecting plate (11a), a portion of the first connecting plate (11a) protrudes axially to form a first protrusion (11c), the first connecting plate (11a) radially abuts against a portion of the sidewall of the condenser-evaporator module (2); the first protrusion (11c) is provided with the air outlet (11b-1a), and the first flow channel pipe (11b) is disposed on the first connecting plate (11a).

7. The refrigerant refrigeration cycle device according to claim 6, characterized in that, The first flow channel pipe (11b) is disposed on the axial end face of the compressor housing (1), and the first flow channel pipe (11b) has an outlet (11b-1a); the condensation inlet (231a) is connected to the outlet (11b-1a), and the outlet (11b-1a) is disposed on the surface of the first connecting plate (11a) that abuts against the condensation evaporation module (2).

8. The refrigerant refrigeration cycle device according to claim 7, characterized in that, The first flow channel (11b) also has a second port (11b-1b), and the second port (11b-1b) is provided with a first sensor (61).

9. The refrigerant refrigeration cycle device according to claim 8, characterized in that, The first flow channel (11b) has a first pipe section (11b-1) and a second pipe section (11b-2), the first pipe section (11b-1) and the second pipe section (11b-2) are arranged at an angle, and the second port (11b-1b) is located at the position where the first pipe section (11b-1) and the second pipe section (11b-2) meet.

10. The refrigerant refrigeration cycle device according to claim 6, characterized in that, The compressor housing (1) also includes a scroll housing section (12) connected to the high-pressure housing section (11), and a portion of the surface of the scroll housing section (12) radially abuts against the condensation and evaporation module (2); The vortex shell section (12) is constructed with a second refrigerant sub-channel (122b-1c), the second refrigerant sub-channel (122b-1c) having a third port (122b-1b), the third port (122b-1b) being connected to the condenser outlet (231b) of the condenser (21), the third port (122b-1b) being located on the surface of the vortex shell section (12) that radially abuts the condenser-evaporation module (2).

11. The refrigerant refrigeration cycle device according to claim 10, characterized in that, The condenser shell (21a) is projected in a direction perpendicular to the sealing plate (23) to form a first projection on the sealing plate (23), the first projection being a quadrilateral. The condensation inlet (231a) and the condensation outlet (231b) are arranged along the diagonal of the first projection.

12. The refrigerant refrigeration cycle device according to claim 10, characterized in that, The evaporator (22) further includes an evaporation inlet (231d) and an evaporation outlet (231c). The evaporation inlet (231d) is connected to the condensation outlet (231b) through a portion of the second refrigerant flow channel, and the evaporation outlet (231c) is connected to the air inlet (134a-5b) through a portion of the second refrigerant flow channel. The evaporating shell (22a) is projected in a direction perpendicular to the sealing plate (23) to form a second projection on the sealing plate (23), the second projection being a quadrilateral; The condensation inlet (231a) and the condensation outlet (231b) are located on the same side of the second projection in the height direction.

13. A thermal management system, characterized in that, Includes the refrigerant refrigeration cycle device according to any one of claims 1-12.

14. A vehicle, characterized in that, Includes the thermal management system as described in claim 13.

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