CN214403974U - Compressor - Google Patents

Abstract

The present application provides a compressor, which includes: a female rotor and a male rotor, the female rotor and the male rotor each having a plurality of teeth, the female rotor and the male rotor each having an exhaust end face, the plurality of teeth forming respective tooth end faces on the exhaust end faces, the tooth end faces being defined by tooth end face contours; the housing has a discharge end mating face provided with at least one refrigerant passage outlet, each of the at least one refrigerant passage outlets having a pair of outlet side edges arranged in a rotational direction of a corresponding one of the female and male rotors; during rotation of the female or male rotor, the refrigerant channel outlet can be completely obscured by the tooth end face of the respective one of the female or male rotor, and the pair of outlet side edges can at least partially simultaneously coincide with the tooth end face contour of the respective one of the female or male rotor. The compressor that this application provided can improve the efficiency of economic ware.

Description

Compressor

Technical Field

The application provides a compressor, in particular to a double-screw compressor applied to a refrigerating system.

Background

The twin-screw compressor has a pair of male and female rotors capable of meshing with each other, and compresses a refrigerant by relative rotation of the pair of male and female rotors. The twin screw compressor communicates with an economizer system that provides a portion of the refrigerant (or other medium) to the interior of the compressor to increase the capacity of the twin screw compressor.

SUMMERY OF THE UTILITY MODEL

The present application provides a twin screw compressor that can obtain refrigerant from an economizer system in a near continuous manner, thereby resulting in a smoother compressor operation.

The compressor includes:

a female rotor and a male rotor each having a plurality of teeth, the female and male rotors each being rotatable about a respective axis and being engaged by the plurality of teeth to compress refrigerant, the female and male rotors each having a discharge end face on which the plurality of teeth form respective tooth end faces defined by tooth end face contours; a housing in which the female and male rotors are disposed, the housing having a discharge end mating face with which a discharge end face of the discharge end mates to form a compression space in cooperation with the female and male rotors and other portions of the housing; at least one refrigerant channel in communication with the compressor economizer system, the at least one refrigerant channel configured to deliver refrigerant in the economizer system into the compression space, each of the at least one refrigerant channel having a refrigerant channel outlet, each of the refrigerant channel outlets being disposed on the discharge end mating face in correspondence with one of the female and male rotors, each of the refrigerant channel outlets having a pair of outlet side edges arranged in a direction of rotation of the respective one of the female and male rotors; wherein a tooth end face contour line of each of the refrigerant passage outlets and the tooth end face is configured to: during rotation of the female or male rotor, the refrigerant passage outlet can be completely blocked by the tooth end face of the respective one of the female or male rotor, and the pair of outlet side edges can at least partially simultaneously coincide with the tooth end face contour line of the respective one of the female or male rotor.

The compressor as described above, the refrigerant passage outlet is completely blocked by the tooth end face of the corresponding one of the female rotor or the male rotor at a timing at which the pair of outlet side edges coincide with the tooth end face contour lines of the corresponding one of the female rotor or the male rotor at least partially at the same time during the rotation of the female rotor or the male rotor.

In the compressor as described above, the tooth end surface contour line coincides with a profile of the teeth of the corresponding one of the female rotor and the male rotor.

In the compressor as described above, the contour lines of the pair of outlet side edges coincide with the profile of the teeth of the corresponding one of the female rotor and the male rotor.

The compressor as described above, the tooth end face contour line having a pair of tooth end face side edges arranged along a rotational direction of the corresponding one of the female rotor and the male rotor, at least one of the pair of tooth end face side edges having a deviating section that deviates inward from a profile line of the corresponding tooth; wherein when the pair of outlet side edges are at least partially simultaneously coincident with the tooth end face contour of the respective one of the female or male rotors, at least one of the pair of outlet side edges is coincident with at least one of the respective pair of tooth end face side edges at the offset section.

The compressor as described above, the discharge ends of the female and male rotors further comprising at least one drainage groove, each of the at least one drainage groove being formed recessed inward from a plane in which the discharge end face lies, each of the at least one drainage groove having an open end communicating with the interdental space and a closed end opposite to the open end, a top of the drainage groove forming a groove contour line on the discharge end face, the sheave contour line including a groove closed end contour line corresponding to the closed end, the offset sections of the pair of tooth end face side edges being formed by the groove closed end contour line.

The compressor as described above, the at least one drainage groove includes a pair of drainage grooves, the pair of drainage grooves are respectively located on both sides of the crest of one tooth, and a pair of outlet side edges of the refrigerant channel outlet can coincide at least partially simultaneously with groove closed end contour lines of the pair of drainage grooves.

In the compressor as described above, the at least one of the drainage grooves includes one drainage groove located on one side of the crest of the corresponding tooth, and one of a pair of outlet side edges of the refrigerant passage outlet may at least partially coincide with the groove-closed end contour line of the one drainage groove.

As with the compressor described above, each of the at least one refrigerant passages includes an outlet section extending from the refrigerant passage outlet to the interior of the shell.

In the compressor as described above, the at least one refrigerant passage includes a plurality of refrigerant passages, and the refrigerant passage outlets of a part of the plurality of refrigerant passages correspond to the tooth end surfaces of the female rotor, and the refrigerant passage outlets of another part of the plurality of refrigerant passages correspond to the tooth end surfaces of the male rotor.

The compressor in the application can enable the economizer to provide the refrigerant in a nearly continuous mode, so that the efficiency of the economizer is effectively improved; and simultaneously, the auxiliary pressure fluctuation caused by periodically blocking the outlet when the tooth end surface of the female rotor or the male rotor sweeps the refrigerant outlet is reduced, so that the pressure pulsation magnitude in the economizer supply pipeline is in a small range, and the integral vibration and noise of the compressor are reduced.

Drawings

FIG. 1A is a perspective view of a compressor of the present application;

FIG. 1B is a cross-sectional view of the compressor of FIG. 1A;

FIG. 2A is a perspective view of the male rotor of FIG. 1B;

FIG. 2B is a side view of the male rotor of FIG. 2A;

FIG. 2C is a perspective view of the female rotor of FIG. 1B;

FIG. 2D is a side view of the female rotor of FIG. 2C;

FIG. 3A is another cross-sectional view of the compressor of FIG. 1A;

FIG. 3B is an enlarged view of a portion of the refrigerant channel of FIG. 3A;

FIG. 4A is a perspective view of the rear housing and female rotor of the compressor of the first embodiment of the present application;

FIG. 4B is a perspective view of the rear housing of FIG. 4A;

FIG. 5A is a schematic illustration of the relative positions of the refrigerant channel outlet and tooth end surfaces of FIG. 4B at a first time;

FIG. 5B is a schematic illustration of the relative positions of the refrigerant channel outlet and the tooth end surfaces of FIG. 4B at a second time;

FIG. 5C is the relative position of the refrigerant channel outlet and tooth end face of FIG. 4B at a third time;

FIG. 6A is a perspective view of the rear housing and female rotor of the compressor of the second embodiment of the present application;

FIG. 6B is a perspective view of the rear housing of FIG. 6A;

FIG. 7A is a rear housing perspective view of a compressor of a third embodiment of the present application;

FIG. 7B is a perspective view of the male rotor of the third embodiment of the present application;

FIG. 7C is a side view of the male rotor of FIG. 7B;

FIG. 8A is a perspective view of the rear housing of the compressor of the fourth embodiment of the present application;

fig. 8B is a perspective view of a female rotor of the fourth embodiment of the present application.

Detailed Description

Various embodiments of the present application will now be described with reference to the accompanying drawings, which form a part hereof. It should be understood that although directional terms, such as "front," "back," "upper," "lower," "left," "right," "inner," "outer," "top," "bottom," "front," "back," "proximal," "distal," "transverse," "longitudinal," and the like may be used herein to describe various example features and elements of the disclosure, these terms are used herein for convenience in the description and are intended to be based on the example orientations shown in the figures. Because the embodiments disclosed herein can be arranged in a variety of orientations, these directional terms are used for purposes of illustration only and are not to be construed as limiting.

Ordinal terms such as "first" and "second" are used herein only for distinguishing and identifying, and do not have any other meanings, unless otherwise specified, either by indicating a particular sequence or by indicating a particular relationship. For example, the term "first component" does not itself imply the presence of a "second component", nor does the term "second component" itself imply the presence of a "first component".

Fig. 1A is a perspective view of a compressor in the present application, and fig. 1B is a cross-sectional view of the compressor in fig. 1A, and as shown in fig. 1A and 1B, a compressor 100 includes a housing 101 and a male rotor 102 and a female rotor 103 in the housing 101. The male rotor 102 and the female rotor 103 can be driven to rotate. The male rotor 102 has a male rotor body 120 and male rotor coupling portions 128 and 129, the male rotor coupling portions 128 and 129 being located at both ends of the male rotor body 120 in the axial direction, the male rotor coupling portion 129 being pivotally coupled to the housing 101, the male rotor coupling portion 128 being drivingly connected to the motor 140 such that the motor 140 can drive the male rotor 102 to rotate relative to the housing 101 about the axis of the male rotor 102. Similarly, the female rotor 103 has a female rotor main body 130 and female rotor connecting portions 138 and 139, the female rotor connecting portions 138 are located at both ends in the axial direction of the female rotor main body 130, the female rotor connecting portions 139 and the female rotor connecting portions 139 are respectively pivoted with the housing 101, and the female rotor 103 can be driven by the male rotor 102 so as to rotate relative to the housing 101 about the axis of the female rotor 103. The male rotor body 120 has a plurality of helical teeth 168 and helical grooves formed between adjacent teeth 168 on the outside thereof, and the male rotor body 120 also has a plurality of helical teeth 169 and helical grooves formed between adjacent teeth 169 on the outside thereof. The teeth 168 and grooves of the male rotor body 120 and the grooves and teeth 169 of the female rotor body 130 form an intermeshing structure such that the male rotor body 120, the female rotor body 130 and the housing 101 together form a compression space 105. The casing 101 has a suction port 121 and a discharge port 122, and refrigerant enters the compressor through the suction port 121, is compressed, and is discharged through the discharge port 122. A refrigerant passage 302 (see fig. 3A) is provided in the housing 101 for supplying refrigerant into the compression space 105 of the compressor 100. The refrigerant passage inlet 141 is located at the outside of the casing 101 for connection with an economizer system that introduces a part of refrigerant in the refrigeration cycle system back to the compressor to increase the capacity of the compressor. For example, the economizer system communicates refrigerant passage 302 with the condenser bottom or subcooler from which a small portion of refrigerant liquid is directed back to the compressor, which can utilize the natural pressure differential to enter the compressor.

The housing 101 includes a front housing 171, a middle housing 172, and a rear housing 173. The front housing 171, the middle housing 172 and the rear housing 173 are connected in sequence. The male rotor body 120 and the female rotor body 130 are located in a middle housing 172, the suction port 121 is provided on a front housing 171, and the discharge port 122 is provided on a rear housing 173. The refrigerant passage inlet 141 is located on the rear housing 173.

Along the axial direction of the male rotor 102 and the female rotor 103, the male rotor body 120 has a suction end 111 and a discharge end 113, and the female rotor body 130 also has a suction end 112 and a discharge end 114. As the male and female rotors 102 and 103 rotate, the refrigerant gas gradually flows from the suction ends 111 and 112 toward the discharge ends 113 and 114. The volume of the compression space 105 is gradually reduced as the male rotor 102 and the female rotor 103 rotate, and the gas in the compression space 105 is gradually compressed. The compressed gas flows from the discharge ends 113 and 114 to the discharge port 122 of the compressor.

Fig. 2A is a perspective view of the male rotor of fig. 1B, and fig. 2B is a side view of the male rotor of fig. 2A, as shown in fig. 2A and 2B, the discharge end 113 of the male rotor 102 has a discharge end face 203. The exhaust end face 203 includes a center end face 215 and a tooth end face 218, and the center end face 215 and the tooth end face 218 are on the same plane. The tooth end face 218 is formed by a plurality of teeth 169 of the male rotor 102, the tooth end face 218 having a tooth end face contour 221, the tooth end face contour 221 coinciding with the profile of the male rotor. Each tooth of the male rotor has a tooth top 231 and a tooth bottom 232, wherein the tooth top 231 is furthest with respect to the central axis of the screw rotor and the tooth bottom 232 is closest with respect to the central axis of the screw rotor. The central end face 215 is generally annular, and the outer side of the central end face 215 coincides with the point of the tooth bottom 232 on the tooth end face contour line 221. In fig. 2A, dashed line 285 illustrates the boundary of central end face 215 and tooth end face 218. On the tooth end face 218, the tooth bottom 232 is the connection point of two adjacent teeth. The inner side of the central end surface 215 is connected to the male rotor connecting portion 128, and the male rotor connecting portion 128 is provided protruding from the discharge end surface 203 for connection to the compressor housing 101. The tooth end surface 218 includes a plurality of tooth end surface portions 281, each tooth end surface portion 281 being formed by an end surface of a corresponding each tooth, and each tooth end surface portion 281 being identical in shape. The tooth end face contour line 221 has a plurality of pairs of tooth end face side edges, and each pair of tooth end face side edges 234 and 236 is located on both sides of each tooth end face portion 281, respectively, and is arranged along the rotational direction of the male rotor 102. The adjacent teeth of the male rotor 102 form inter-tooth spaces 291 therebetween, and the inter-tooth spaces 291 can form a part of the compression space 105 with the housing 101 and the teeth 169 of the female rotor 103.

Fig. 2C is a perspective view of the female rotor of fig. 1B, and fig. 2D is a side view of the female rotor of fig. 2C, with the discharge end 114 of the female rotor 103 having a discharge end face 204, similar to the male rotor 102, with the discharge end face 204 including a central end face 217 and a tooth end face 219. Each tooth of female rotor 103 also has a tooth top 238 and a tooth bottom 239. In fig. 2D, dashed line 286 illustrates the interface of the central end face 217 and the tooth end face 219. The tooth end face 219 has a tooth end face contour 222. The tooth end face 219 includes a plurality of tooth end face portions 282, each tooth end face portion 282 being formed by an end face of each tooth, each tooth end face portion 282 being identical in shape. The tooth end face profile 221 at each tooth end face portion 282 has a pair of tooth end face side edges 235 and 237. The adjacent teeth of the female rotor 103 form inter-tooth spaces 292 therebetween, and the inter-tooth spaces 292 can form a part of the compression space 105 with the housing 101 and the teeth 168 of the male rotor 102.

Referring to fig. 1A-2D, housing 101 has a discharge end mating surface 151 and a rotor body mating surface 152 therein. The discharge end mating face 151 is formed by one side of the rear housing 173, and the rotor body mating face 152 is formed by the inner side of the middle housing 172. The outer sides of the axial direction of the male rotor body 120 and the female rotor body 130 are fitted with the rotor body fitting surfaces 152, and the gas discharge end surfaces 203 and 204 of the male rotor body 120 and the female rotor body 130 are fitted with the gas discharge end fitting surfaces 151, so that the male rotor body 120 and the female rotor body 130, the gas discharge end fitting surfaces 151, and the rotor body fitting surfaces 152 enclose the compression space 105. The mating of the discharge end mating face 151 and the rotor body mating face 152 with the male rotor body 120 and the female rotor body 130 means that there is little clearance between or contact so that the compressed gas in the compression space 105 can hardly leak out, thereby enabling the gas to be compressed.

Fig. 3A is another sectional view of the compressor of fig. 1A, showing a refrigerant passage, and fig. 3B is a partially enlarged view of the refrigerant passage of fig. 3A. As shown in fig. 3A, a refrigerant passage 302 having a refrigerant passage inlet 141 and a refrigerant passage outlet 342 is provided in the rear housing 173, the refrigerant passage outlet 342 is provided on the discharge end fitting surface 151, and the refrigerant passage inlet 141 is provided on the outer surface of the housing 101. The refrigerant passage outlet 342 is positioned to correspond to the position of the tooth end surface 218 or 219 such that the tooth end surface 218 or 219 periodically sweeps the refrigerant passage outlet 342 during rotation of the female and male rotors 103 and 102. The refrigerant channel 302 includes an outlet section 322 and a main body section 325, the outlet section 322 having a refrigerant channel outlet 342 formed extending toward the inside of the casing 101, the main body section 325 being connected to the outlet section 322, and a flow area of the main body section 325 being smaller than that of the outlet section 322. As the fluid in the refrigerant channel 302 passes from the main section 325 into the outlet section 322, the flow rate decreases. In this embodiment, the inner diameter of the outlet section 322 is uniform, so that the junction of the main body section 325 and the outlet section 322 forms a step. In another embodiment, the inner diameter of the outlet section 322 may become gradually larger from the inside to the outside. In yet another embodiment, the main section 325 may also have the same flow area as the outlet section 322.

Fig. 4A is a perspective view of the rear housing and the female rotor of the compressor of the first embodiment of the present application. Fig. 4B is a perspective view of the rear housing of fig. 4A. Showing the relationship of the refrigerant channel outlet 342 to the discharge end face 204 of the female rotor 103. In fig. 4A, in order to clearly illustrate the relationship of the female rotor 103 with the refrigerant passage outlet 342, the female rotor 103 is disposed at a distance from the rear housing 173 to show the refrigerant passage outlet 342. Inside the compressor 100, the discharge end face 204 of the female rotor 103 is disposed immediately adjacent to the discharge end mating face 151.

As shown in fig. 4B, the refrigerant passage outlet 342 is generally circular, the interior of the refrigerant passage outlet 342 showing the profile of the body section 325, and the area of the refrigerant passage outlet 342 is greater than the cross-sectional area of the body section 325 of the refrigerant passage 302. The refrigerant passage outlet 342 has a pair of outlet side edges 431 and 432, and the outlet side edges 431 and 432 are oppositely arranged in the rotating direction of the female rotor 103. The refrigerant passage outlet 342 is provided to be completely shielded by the tooth end surface 219 during the rotation of the female rotor 103. The exit-side edge 431 has a first point 451 thereon and the exit-side edge 432 has a second point 452 thereon. The first point 451 and the second point 452 can simultaneously coincide with the tooth end profile 222 of the female rotor 103, i.e. with the profile of the female rotor 103, at a position where the refrigerant passage outlet 342 is completely blocked by the tooth end 219. That is, at least two points located on the outlet- side edges 431 and 432, respectively, coincide with the tooth-end-face contour line 222 at the position where the refrigerant passage outlet 342 is completely blocked by the tooth end face 218, but a plurality of points located on the outlet- side edges 431 and 432, respectively, may coincide with the tooth-end-face contour line 222.

Fig. 5A is a schematic view of the relative position of the refrigerant channel inlet and the tooth end surface at a first time in fig. 4B, fig. 5B is a schematic view of the relative position of the refrigerant channel inlet and the tooth end surface at a second time in fig. 4B, and fig. 5C is a schematic view of the relative position of the refrigerant channel inlet and the tooth end surface at a third time in fig. 4B, showing the relative position of the female rotor and the refrigerant channel inlet during rotation. In fig. 5A to 5C, a part of the tooth end face contour line 221 of the female rotor is shown by a dotted line.

As shown in fig. 5A to 5C, at the first timing, as shown in fig. 5A, in the counterclockwise direction, the outlet-side edge 431 of the refrigerant channel outlet 342 is located downstream of the tooth end face side edge 235 of the female rotor 103, and the outlet-side edge 432 of the refrigerant channel outlet 342 is located downstream of the tooth end face side edge 237 of the female rotor 103. So that the portion of the refrigerant passage outlet 342 near the outlet side edge 431 is blocked by the tooth end face 219 and the portion of the refrigerant passage outlet 342 near the outlet side edge 432 is offset from the tooth end face 219 and outwardly beyond the tooth end face 219 so that the refrigerant passage outlet 342 near the outlet side edge 432 communicates with the compression space 105 between two teeth, and the refrigerant in the refrigerant passage 302 can enter the compression space 105.

At the second timing, as shown in fig. 5B, the outlet side edge 431 of the refrigerant channel outlet 342 partially coincides with the tooth end face side edge 235 of the female rotor 103, while the outlet side edge 432 of the refrigerant channel outlet 342 partially coincides with the tooth end face side edge of the female rotor 103. The refrigerant passage outlet 342 is completely blocked by the tooth end face 219, and the refrigerant in the refrigerant passage 302 cannot enter the compression space 105.

At the third timing, as shown in fig. 5C, in the counterclockwise direction, the outlet side edge 431 of the refrigerant channel outlet 342 is located upstream of the tooth end face side edge 235 of the female rotor 103, and the outlet side edge 432 of the refrigerant channel outlet 342 is located upstream of the tooth end face side edge 237 of the female rotor 103. So that the portion of the refrigerant passage outlet 342 near the outlet side edge 431 is offset from the tooth end face 219 and outwardly beyond the tooth end face 219, and the portion of the refrigerant passage outlet 342 near the outlet side edge 432 is blocked by the tooth end face 219, so that the refrigerant passage outlet 342 near the outlet side edge 431 communicates with the compression space 105 between two teeth, and the refrigerant in the refrigerant passage 302 can enter the compression space 105.

In the present application, the refrigerant passage outlet 342 is shaped such that the female rotor 103 is completely shielded by the tooth end surface 218 only at the second timing as shown in fig. 5B during the rotation of the female rotor 103, and the total time used at the second timing occupies a very small proportion, for example, 0.1% or less, during one rotation of the female rotor 103. That is, during the rotation of the female rotor 103, the refrigerant passage outlet 342 is also communicated with the compression space 105 most of the time, which makes the process of supplying the refrigerant to the female rotor 103 and the male rotor 102 by the refrigerant passage 302 close to a continuous process. This enables the refrigerant in the economizer system to be supplied into the compression space 105 as much as possible, increasing the amount of refrigerant participating in compression per unit time in the compressor, thereby increasing the operating efficiency of the compressor. And through a plurality of experiments and observations of the inventor, if the refrigerant channel outlet 342 and the compression space 105 are intermittently communicated and disconnected during one rotation of the male rotor 102 and the female rotor 103, namely, the proportion of the time that the refrigerant channel outlet 342 is completely shielded by the tooth end surfaces 218 and 219 to one rotation of the male rotor 102 and the female rotor 103 is larger, additional pressure fluctuation in the refrigerant channel 302 is easily caused by periodically blocking the refrigerant channel outlet 342, so that the compressor 100 generates certain noise, and the scheme provided by the invention can reduce the noise. In addition, the refrigerant passage 302 of the present application enables the process of supplying the lubricating refrigerant to approach a continuous process, and also enables the operation process of the male rotor 102 and the female rotor 103 to be smoother. During operation of the compressor 100, the pressures in two adjacent compression spaces 105 are not the same. In the present application, the refrigerant passage outlet 342 can communicate with only one compression space 105 but not with two adjacent compression spaces 105 at the same time during the entire rotation of the female rotor 103, and thus the two adjacent compression spaces 105 are not in fluid communication through the refrigerant passage outlet 342, and thus a leakage phenomenon does not occur, so that it is possible to avoid affecting the operation efficiency of the compressor 100.

Fig. 6A is a perspective view of the rear housing and female rotor of the compressor of the second embodiment of the present application. Fig. 6B is a perspective view of the rear housing of fig. 6A. The embodiment shown in fig. 6A and 6B is similar to the embodiment shown in fig. 4A and 4B, except that the shape of the refrigerant channel outlet 642 is different. Similarly, in fig. 6A, in order to clearly illustrate the relationship of the female rotor 103 with the refrigerant passage outlet 642, the female rotor 103 is disposed at a distance from the rear housing 173 to show the refrigerant passage outlet 642. Inside the compressor 100, the discharge end face 204 of the female rotor 103 is disposed immediately adjacent to the discharge end mating face 151.

As shown in fig. 6B, the refrigerant passage outlet 642 is irregularly shaped, a portion of the contour line of the refrigerant passage outlet 642 substantially conforms to the shape of the profile of the teeth of the female rotor, and the inner ring 680 of the refrigerant passage outlet 642 shows the contour of the body segment 325, and the area of the refrigerant passage outlet 642 is larger than the area of the cross-section of the body segment 325 of the refrigerant passage 302. The refrigerant passage outlet 642 has a pair of outlet side edges 631 and 632, and the outlet side edges 631 and 632 are oppositely disposed to be arranged along the rotation direction of the female rotor 103. The refrigerant passage outlet 642 is provided such that the refrigerant passage outlet 642 can be completely blocked by the tooth end face 219 during rotation of the female rotor 103. At the position where the refrigerant passage outlet 642 is completely blocked by the tooth end face 219, the contour of the outer side of the refrigerant passage outlet 342 coincides with the tooth end face contour line 222 of the male rotor 102, i.e., the profile of the male rotor 102. That is, at the position where the refrigerant passage outlet 642 is completely blocked by the tooth end face 219, the pair of outlet side edges 631 and 632 coincide with the tooth end face contour line 222, and then the outlet side edges 631 and 632 coincide with the pair of tooth end face side edges 235, 237. The embodiment shown in fig. 6A and 6B can achieve the same technical effects as the embodiment shown in fig. 4A and 4B.

In addition to the embodiments shown in fig. 4A-4B and 6A-6B, the refrigerant passage outlet may have other shapes as long as it is satisfied that at least two points of the pair of outlet side edges coincide with the pair of tooth end face side edges, respectively, when the refrigerant passage outlet is completely blocked. The refrigerant passage outlet may be disposed to correspond to the male rotor, and may also be disposed to correspond to the female rotor. Further, the refrigerant passage may be provided in plural numbers, and correspond to different teeth in the male rotor or the female rotor.

Fig. 7A is a rear housing perspective view of a compressor of a third embodiment of the present application. Fig. 7B is a perspective view of a male rotor of a third embodiment of the present application, and fig. 7C is a side view of the male rotor of fig. 7B. The embodiment shown in fig. 7A-7C is similar to the embodiment shown in fig. 4A-4B, except that the shape of the tooth end faces is different from the shape of the refrigerant channel outlets.

As shown in fig. 7A, the dotted line indicates the shape of the profile 708 of the male rotor, the refrigerant passage outlet 742 has a substantially circular shape, the area of the refrigerant passage outlet 742 is smaller than the area of the region defined by the profile of the male rotor, and the outside of the refrigerant passage outlet 742 can be spaced from the profile 708 of the male rotor. The refrigerant passage outlet 742 has a pair of outlet side edges 731 and 732, and the outlet side edges 731 and 732 are oppositely disposed to be arranged in the rotational direction of the male rotor 102. In this embodiment, the outlet section of the refrigerant channel is the same inner diameter as the main body section.

As shown in fig. 7B and 7C, the tooth end face 718 of the male rotor 102 has a tooth end face contour 721, and the tooth end face contour 721 has a pair of tooth end face- side edges 743 and 744 arranged along the rotation direction of the male rotor 102. Each tooth of the discharge end 113 of the male rotor 102 includes a pair of drainage grooves 705 and 706, each of the drainage grooves 705 and 706 being formed recessed inwardly from the plane of the discharge end face 203, i.e., the bottom of the drainage grooves 705 and 706 lie in a plane that is lower than the plane of the discharge end face 203. The drainage grooves 705 and 706 are located on either side of the crest 231 of one tooth of the male rotor. Drainage channel 705 has an open end 745 in communication with the interdental spaces and a closed end 746 opposite open end 745, and drainage channel 706 has an open end 748 in communication with the interdental spaces and a closed end 747 opposite open end 748, with the closed end 746 and closed end 747 being spaced apart such that communication between drainage channels 705 and 706 is not possible.

The tops of the drainage slots 705 and 706 form slot contours 761 and 762 in the discharge end face 203, the sheave contours 761 and 762 forming part of the tooth end face contour 721. That is, one portion of the tooth end profile 721 coincides with the profile of the male rotor 102 and the other portion of the sheave profiles 761 and 762 coincides. Sheave profiles 761 and 762 include slot closed end profiles 768 and 769 corresponding to the closed ends 746 and 747, with slot closed end profiles 768 and 769 forming offset sections 753, 754 of tooth face profile 721. The offset segments 753 and 754 offset inwardly from the profile of the teeth of the male rotor.

In fig. 7C, the shape of the refrigerant passage outlet 742 is illustrated by a dotted line. The shape of the offset sections 753 and 754 matches the shape of the refrigerant channel outlet 742, the refrigerant channel outlet 742 can be completely blocked by the toothed end face 718 during rotation of the male rotor 102. At a position where the refrigerant passage outlet 742 is completely blocked by the tooth end face 718, a pair of outlet side edges 731 and 732 of the refrigerant passage outlet 742 coincide with the groove-closed end contours 768 and 769 of the male rotor 102. That is, at the position where the refrigerant passage outlet 742 is completely blocked by the tooth end face 718, the pair of outlet- side edges 731 and 732 each coincide with the offset sections 753, 754 of the tooth end face contour 721. When the outlet-side edge 731 of the refrigerant passage outlet 742 is deviated in the clockwise direction from the deviated section 753 of the tooth end face contour line 721, the refrigerant passage outlet 742 communicates with the compression space 105 through the flow guide groove 705, and the refrigerant in the refrigerant passage can enter the compression space 105. When the offset section 754 of the tooth end contour 721 is offset in the clockwise direction from the outlet-side edge 732 of the refrigerant passage outlet 742, the refrigerant passage outlet 742 communicates with the compression space 105 through the drainage groove 706. The shape and relative position of the drainage grooves 705 and 706 on each tooth of the discharge end 113 is the same so that the refrigerant channel coincides with the respective offset sections 753 and 754 as the corresponding tooth end portion of each tooth passes through the refrigerant channel outlet. In the embodiment shown in fig. 7A to 7C, the refrigerant passage outlet 742 is disconnected from the compression space 105 only at a specific time during one rotation of the male rotor 102, and a process of supplying the refrigerant almost continuously can be similarly achieved, and the same technical effects as those of the embodiment shown in fig. 4A and 4B can be achieved.

In other embodiments of the present application, the refrigerant passage outlet 742 need only coincide somewhat with the offset sections 753 and 754, respectively, at the outlet- side edges 731 and 732 where they are completely obscured by the tooth end face 718. The drainage grooves in the present application may also be arranged on the female rotor 103 to cooperate with the refrigerant channel outlet at the female rotor 103. The refrigerant passage may be plural and correspond to different teeth. In another embodiment, the drainage slots may extend obliquely from the closed end to the open end toward the interior of the male rotor, such that the closed end is flush with the exhaust end face and the open end is lower than the exhaust end face.

Fig. 8A is a rear housing perspective view of a compressor of a fourth embodiment of the present application. Fig. 8B is a perspective view of a female rotor of the fourth embodiment of the present application. The embodiment shown in fig. 8A-8B is similar to the embodiment shown in fig. 7A-7B, except that the drainage slots are arranged on the female rotor, one for each tooth.

As shown in fig. 8A, the dotted line indicates the shape of the profile 808 of the female rotor, the refrigerant passage outlet 842 is substantially circular, the area of the refrigerant passage outlet 842 is smaller than the area of the region defined by the profile of the female rotor, and the outer side of the refrigerant passage outlet 842 can be spaced from the profile 808 of the female rotor. The refrigerant passage outlet 842 has a pair of outlet side edges 831 and 832, and the outlet side edges 831 and 832 are oppositely disposed to be arranged along the rotation direction of the female rotor 103. In this embodiment, the outlet section of the refrigerant channel is the same inner diameter as the main body section.

As shown in fig. 8B, the tooth end surface 819 of the female rotor 103 has a tooth end surface profile 822, and the tooth end surface profile 822 has a pair of tooth end surface- side edges 843 and 844 arranged in the rotational direction of the female rotor 103. Each tooth of the discharge end 114 of the female rotor 103 includes a flow guide groove 805, and the flow guide groove 805 is formed by being recessed inward from the plane of the discharge end face 204, that is, the plane of the bottom of the flow guide groove 805 is lower than the plane of the discharge end face 204. The drainage grooves 805 are located on one side of the crests 238 of the teeth of the female rotor 103. The drainage channel 805 has an open end 845 communicating with the interdental space and a closed end 846 opposite the open end 845, the closed end 846 being spaced from the tooth end face contour 822.

The top of the flow director slots 805 form a slot profile 861 in the discharge end face 204, which slot profile 861 forms a portion of the tooth end face profile 822. That is, one portion of the tooth end profile 822 coincides with the profile of the female rotor 103 and the other portion of the sheave profile 861. The sheave profile 861 includes a slot closed end profile line 868 corresponding to the closed end 846, the slot closed end profile line 868 forming an offset section 853 of the tooth end face profile line 822. The offset section 853 inwardly offsets the profile of the teeth of the female rotor 103.

The shape of the offset section 853 matches the shape of the refrigerant passage outlet 842, and the refrigerant passage outlet 842 can be completely blocked by the tooth end surfaces 819 during rotation of the female rotor 103. At a position where the refrigerant passage outlet 842 is completely blocked by the tooth end face 819, a pair of outlet side edges 831832 of the refrigerant passage outlet 842 coincide with the groove-closed end contour line 868 and the tooth end face side edge 844 of the female rotor 103, respectively. That is, where the refrigerant passage outlet 842 is completely blocked by the tooth end surfaces 819, the pair of outlet side edges 831 and 832 each coincide with the offset section 853 of the tooth end surface contour 822 and the tooth end surface side edge 844. When the outlet-side edge 831 of the refrigerant passage outlet 842 is deviated from the deviated section 853 of the tooth end surface contour 822 in the clockwise direction, the refrigerant passage outlet 842 is communicated with the compression space 105 through the drainage groove 805, and the refrigerant in the refrigerant passage can be introduced into the compression space 105. The refrigerant passage outlet 842 directly communicates with the compression space 105 when the tooth-side edge 844 of the tooth-side contour 822 is deviated from the outlet-side edge 832 of the refrigerant passage outlet 842 in the clockwise direction. On each tooth of the female rotor 103, the shape and location of the flow-directing groove 805 is the same so that the refrigerant channel outlet 842 can coincide with the respective offset section 853 and tooth face side edge 844 as the tooth end portion corresponding to each tooth passes the refrigerant channel outlet. In the embodiment shown in fig. 8A-8B, the refrigerant passage outlet 842 is disconnected from the compression space 105 only at a specific time during one rotation of the female rotor 802, and the refrigerant can be supplied nearly continuously, and the same technical effects as in the embodiment shown in fig. 4A and 4B can be achieved.

In other embodiments of the present application, the location outlet- side edges 831 and 832 where the refrigerant passage outlet 842 is completely blocked by the tooth end face 819 need only coincide somewhat with the offset section 853 and the tooth end face-side edge 844, respectively. The flow-directing grooves in the present application may also be disposed on the male rotor 102 to mate with the refrigerant channel outlets at the male rotor 102.

In the application, the number of the refrigerant channels can be multiple, the refrigerant channel outlets of the plurality of the refrigerant channels correspond to different teeth respectively, and the more refrigerant channels enable the economizer system to provide more refrigerant for the compression space in unit time, so that the work efficiency of the compressor is improved.

The arrangement of the refrigerant channel outlets and the arrangement of the female rotor and the male rotor in the application can enable the economizer system to provide refrigerant to the compression space in a near-continuous mode, and the working efficiency of the compressor is improved. Meanwhile, unnecessary pressure fluctuation can be reduced, the noise of the compressor is reduced, and the stable operation of the compressor is ensured. And the design scheme in the application has a simple structure and is easy to process.

While only certain features of the application have been illustrated and described herein, many modifications and changes will occur to those skilled in the art. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the application.

Claims (10)

1. A compressor, characterized by comprising:

a female rotor and a male rotor each having a plurality of teeth, the female and male rotors each being rotatable about a respective axis and being engaged by the plurality of teeth to compress refrigerant, the female and male rotors each having a discharge end face on which the plurality of teeth form respective tooth end faces defined by tooth end face contours;

a housing in which the female and male rotors are disposed, the housing having a discharge end mating face with which a discharge end face of the discharge end mates to form a compression space in cooperation with the female and male rotors and other portions of the housing;

at least one refrigerant channel in communication with the compressor economizer system, the at least one refrigerant channel configured to deliver refrigerant in the economizer system into the compression space, each of the at least one refrigerant channel having a refrigerant channel outlet disposed on the discharge end mating face in correspondence with one of the female and male rotors, the refrigerant channel outlet having a pair of outlet side edges arranged in a direction of rotation of the respective one of the female and male rotors;

wherein the refrigerant channel outlet and a tooth end face contour line of the tooth end face are configured to: during rotation of the female or male rotor, the refrigerant passage outlet can be completely blocked by the tooth end face of the respective one of the female or male rotor, and the pair of outlet side edges can at least partially simultaneously coincide with the tooth end face contour line of the respective one of the female or male rotor.

2. The compressor as set forth in claim 1, wherein:

the refrigerant passage outlet is completely blocked by the tooth end face of the corresponding one of the female rotor or the male rotor at a timing at which the pair of outlet side edges coincide with the tooth end face contour line of the corresponding one of the female rotor or the male rotor at least partially simultaneously during rotation of the female rotor or the male rotor.

3. The compressor as set forth in claim 1, wherein:

the tooth end face contour line coincides with a profile of a tooth of a corresponding one of the female rotor and the male rotor.

4. A compressor as set forth in claim 3, wherein:

the contour lines of the pair of outlet side edges coincide with the profile of the teeth of the corresponding one of the female and male rotors.

5. The compressor as set forth in claim 1, wherein:

the tooth flank profile line has a pair of tooth flank side edges disposed along a direction of rotation of a respective one of the female and male rotors, at least one of the pair of tooth flank side edges having an offset section that is offset inwardly from a profile line of the respective tooth;

wherein when the pair of outlet side edges are at least partially simultaneously coincident with the tooth end face contour of the respective one of the female or male rotors, at least one of the pair of outlet side edges is coincident with at least one of the respective pair of tooth end face side edges at the offset section.

6. The compressor as set forth in claim 5, wherein:

the exhaust end of the female rotor and the exhaust end of the male rotor further comprise at least one drainage groove, each of the at least one drainage groove is formed by inwards sinking from the plane where the exhaust end face is located, each of the at least one drainage groove is provided with an open end communicated with the interdental space and a closed end opposite to the open end, the top of the drainage groove forms a groove contour line on the exhaust end face, the sheave contour line comprises a groove closed end contour line corresponding to the closed end, and the deviation sections of the side edges of the pair of tooth end faces are formed by the groove closed end contour line.

7. The compressor as set forth in claim 6, wherein:

the at least one drainage groove comprises a pair of drainage grooves which are respectively positioned at two sides of the tooth crest of one tooth, and a pair of outlet side edges of the refrigerant channel outlet can be at least partially coincided with the groove closed end contour lines of the pair of drainage grooves.

8. The compressor as set forth in claim 6, wherein:

the at least one drainage groove comprises one drainage groove located on one side of the crest of the corresponding tooth, and one of a pair of outlet side edges of the refrigerant channel outlet can at least partially coincide with the groove-closed end contour line of the one drainage groove.

9. The compressor as set forth in claim 1, wherein:

each of the at least one refrigerant channel includes an outlet section extending from the refrigerant channel outlet to the interior of the shell.

10. A compressor as set forth in claim 9, wherein:

the at least one refrigerant channel includes a plurality of refrigerant channels, refrigerant channel outlets of a part of the plurality of refrigerant channels correspond to the tooth end surfaces of the female rotor, and refrigerant channel outlets of another part of the plurality of refrigerant channels correspond to the tooth end surfaces of the male rotor.

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