Compressor pump body and compressor

Abstract

The utility model discloses a compressor pump body and a compressor. The compressor pump body comprises a crankshaft, a compression mechanism and a connecting piece. The compression mechanism comprises a first bearing, an air cylinder component and a second bearing, the first bearing is provided with a first bearing hole, the second bearing is provided with a second bearing hole, and the side, away from the air cylinder component, of at least one of the first bearing and the second bearing is provided with a plurality of grooves and at least one annular groove. The multiple grooves are formed in the peripheral side of the first bearing or the second bearing at intervals in the circumferential direction of the first bearing hole or the second bearing hole, and the at least one annular groove is formed in the circumferential direction of the first bearing hole or the second bearing hole in a surrounding mode; the multiple connecting pieces are arranged on the peripheral side of the compressing mechanism at intervals in the circumferential direction of the crankshaft, and at least one groove is formed between every two adjacent connecting pieces. The compressor can solve the problems that raw materials of the compressor are wasted and the logistics transportation cost of the compressor is increased due to the fact that the weight of a lower bearing in the compressor in the prior art is large.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of refrigeration equipment, in particular to a compressor pump body and a compressor. BACKGROUND

[0002] A rotary compressor is used to compress refrigerant gas by rotating a piston. The rotary compressor usually includes a crankshaft, an upper bearing, a lower bearing and a cylinder. However, the structure of the lower bearing in the existing rotary compressor is single and heavy, and the heavy weight of the lower bearing will cause waste of raw materials of the compressor and increase the logistics transportation cost of the compressor, which is not conducive to the lightweight design and green energy-saving manufacturing of the compressor product. CONTENT OF THE UTILITY MODEL

[0003] The main purpose of the present application is to provide a compressor pump body and a compressor to solve the problem of heavy weight of the lower bearing in the compressor in the prior art, which causes waste of raw materials of the compressor and increases the logistics transportation cost of the compressor.

[0004] According to one aspect of the present application, a compressor pump body is provided, comprising:

[0005] a crankshaft;

[0006] a compression mechanism, the compression mechanism comprising a first bearing, a cylinder component and a second bearing, the first bearing, the cylinder component and the second bearing being sequentially sleeved on the crankshaft along the axial direction of the crankshaft, the first bearing having a first bearing hole for the crankshaft to pass through, the second bearing having a second bearing hole for the crankshaft to pass through, at least one of the first bearing and the second bearing being provided with a plurality of grooves and at least one annular groove on the side away from the cylinder component, the plurality of grooves being arranged on the outer circumferential side of the first bearing or the second bearing at intervals along the circumferential direction of the first bearing hole or the second bearing hole, and the at least one annular groove being arranged around along the circumferential direction of the first bearing hole or the second bearing hole;

[0007] a plurality of connecting pieces, the plurality of connecting pieces being arranged on the outer circumferential side of the compression mechanism at intervals along the circumferential direction of the crankshaft and sequentially passing through the first bearing, the cylinder component and the second bearing, and at least one of the grooves being arranged between each adjacent two connecting pieces.

[0008] Further, the second bearing is provided with a plurality of grooves and at least one annular groove on the side away from the cylinder component, each annular groove is provided with a rib, and the rib separates the annular groove into a plurality of arc-shaped grooves;

[0009] The length L1 of the arc-shaped groove along the circumferential direction of the second bearing hole and the width L2 of the arc-shaped groove along the radial direction of the second bearing hole satisfy the relationship L1>L2.

[0010] Further, the width D1 of the rib along the circumferential direction of the second bearing hole satisfies the relationship 1mm≤D1≤10mm.

[0011] Further, the number N of the ribs satisfies the relationship 3≤N≤8.

[0012] Further, a plurality of the grooves and the annular grooves are arranged on the side of the second bearing away from the cylinder component, the annular grooves include a plurality of annular grooves, and the plurality of annular grooves are arranged in a nested manner along the radial direction of the second bearing hole.

[0013] The second bearing is provided with a plurality of the grooves and at least one annular groove on the side away from the cylinder component, each of the grooves extends in a direction away from the second bearing hole and penetrates the outer circumferential surface of the second bearing along the radial direction of the second bearing hole.

[0014] Further, the second bearing is provided with a plurality of the grooves and at least one annular groove on the side away from the cylinder component, and the second bearing is provided with a mounting hole through which the connecting member passes.

[0015] The maximum thickness H1 between the annular groove and the side of the second bearing close to the cylinder component and the thickness H2 of the mounting hole satisfy the relationship 1.04≤H2 / H1≤1.39 along the axial direction of the second bearing hole.

[0016] Further, the second bearing is provided with a plurality of the grooves and at least one annular groove on the side away from the cylinder component.

[0017] The maximum thickness H1 between the annular groove and the side of the second bearing close to the cylinder component and the minimum thickness H3 between the annular groove and the side of the second bearing close to the cylinder component satisfy the relationship 1.0≤H1 / H3≤1.4 along the axial direction of the second bearing hole.

[0018] Further, the second bearing is provided with a plurality of the grooves and at least one annular groove on the side away from the cylinder component.

[0019] The maximum thickness H1 between the annular groove and the side of the second bearing close to the cylinder component and the minimum thickness H4 between the bottom of the groove and the side of the second bearing close to the cylinder component satisfy the relationship 1.0≤H1 / H4≤5.0 along the axial direction of the second bearing hole.

[0020] Further, the maximum thickness H1 between the annular groove and the second bearing close to the side of the cylinder part along the axial direction of the second bearing hole satisfies the relationship: 5.0mm≤H1≤6.6mm.

[0021] Further, the sum V1 of the volumes of the plurality of grooves and the at least one annular groove satisfies the relationship: 0.15≤V1 / V≤0.35 with the volume V of the first bearing or the second bearing; and / or,

[0022] The sum V2 of the volumes of the plurality of annular grooves satisfies the relationship: 0.0015≤V2 / V≤0.025 with the volume V of the first bearing or the second bearing; and / or,

[0023] In the projection of the crankshaft in the axial direction, the projection of the groove comprises at least one of a rectangle, a trapezoid, a circle and a diamond.

[0024] In another aspect, the application further provides a compressor comprising the compressor pump body described above.

[0025] Since at least one of the first bearing and the second bearing in the application is provided with a plurality of grooves and at least one annular groove away from the side of the cylinder part, this not only does not affect the sealing of the first bearing, the cylinder part and the second bearing after assembly, but also can reduce the weight of at least one of the first bearing and the second bearing, save the consumption of raw materials required when manufacturing the first bearing or the second bearing, thereby reducing the manufacturing cost and transportation cost of the compressor with the first bearing and the second bearing, realizing the lightweight design and green energy-saving manufacturing of the compressor product, and having good social and economic value. BRIEF DESCRIPTION OF DRAWINGS

[0026] The accompanying drawings, which are included to provide a further understanding of the application and constitute a part of this application, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:

[0027] Figure 1 A sectional view of the compressor disclosed in the embodiments of the application;

[0028] Figure 2 A structure schematic view of the first second bearing disclosed in the embodiments of the application;

[0029] Figure 3 A front view of the first second bearing disclosed in the embodiments of the application;

[0030] Figure 4 A side view of the first second bearing disclosed in the embodiments of the application;

[0031] Figure 5 A sectional view of a first second bearing disclosed in embodiments of the present application;

[0032] Figure 6 A structural schematic view of a second second bearing disclosed in embodiments of the present application;

[0033] Figure 7 A side view of a second second bearing disclosed in embodiments of the present application.

[0034] Wherein, the above-mentioned drawings include the following reference signs:

[0035] 10, compressor pump body; 11, crankshaft; 111, eccentric part; 12, compression mechanism; 121, first bearing; 122, cylinder part; 1221, cylinder body; 1222, piston; 123, second bearing; 124, first bearing hole; 125, second bearing hole; 126, groove; 127, annular groove; 128, mounting hole; 129, rib; 13, muffler; 20, shell; 21, exhaust pipe; 30, motor; 31, rotor; 32, stator. DETAILED DESCRIPTION

[0036] It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict. The present application will be described in detail below with reference to the drawings and in combination with the embodiments.

[0037] It should be noted that the terms used herein are only intended to describe specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, the singular form is intended to include the plural form, unless the context clearly indicates otherwise, and it should also be understood that the terms "comprise" and / or "include" as used in the specification indicate the presence of features, steps, operations, devices, components and / or combinations thereof.

[0038] The relative arrangement of components and steps, numerical expressions and values set forth in these embodiments do not limit the scope of the present application, unless otherwise specifically stated. At the same time, it should be understood that the sizes of the various parts shown in the drawings are not drawn in proportion to the actual proportions. Techniques, methods and devices known to those of ordinary skill in the relevant art can not be discussed in detail, but should be considered as part of the authorized specification, if appropriate. In all examples shown and discussed herein, any specific value should be interpreted as merely exemplary, and not as a limitation. Therefore, other examples of exemplary embodiments can have different values. It should be noted that similar reference signs and letters represent similar items in the following drawings, so once an item is defined in one drawing, it does not need to be further discussed in subsequent drawings.

[0039] As mentioned in the background, the structure of the lower bearing in the existing rotary compressor is simple and heavy, and the heavy weight of the lower bearing will cause waste of raw materials of the compressor and increase the logistics transportation cost of the compressor, which is not conducive to the lightweight design and green energy-saving manufacturing of the compressor product. Therefore, the inventors of the present application design a new compressor pump body, which can realize the lightweight design of the lower bearing while maintaining the original mechanical properties of the lower bearing, thereby reducing the consumption of raw materials for manufacturing the lower bearing, thereby solving the problem that the heavy weight of the lower bearing in the compressor will cause waste of raw materials for manufacturing the compressor and increase the logistics transportation cost of the compressor. The compressor pump body of the present application will be described in detail below in combination with the drawings.

[0040] Referring to Figures 1 to 7 According to the embodiment of the present application, a compressor pump body 10 is provided, which comprises a crankshaft 11, a compression mechanism 12 and a connecting piece (not shown in the drawings).

[0041] The compression mechanism 12 comprises a first bearing 121, a cylinder component 122 and a second bearing 123, which are sequentially sleeved on the crankshaft 11 along the axial direction of the crankshaft 11. The first bearing 121 has a first bearing hole 124 through which the crankshaft 11 passes, and the second bearing 123 has a second bearing hole 125 through which the crankshaft 11 passes. At least one of the first bearing 121 and the second bearing 123 is provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122. The plurality of grooves 126 are arranged on the outer circumferential side of the first bearing 121 or the second bearing 123 along the circumferential direction of the first bearing hole 124 or the second bearing hole 125, and the at least one annular groove 127 is arranged along the circumferential direction of the first bearing hole 124 or the second bearing hole 125. The connecting piece comprises a plurality of connecting pieces, which are arranged on the outer circumferential side of the compression mechanism 12 along the circumferential direction of the crankshaft 11 and sequentially pass through the first bearing 121, the cylinder component 122 and the second bearing 123, and at least one groove 126 is arranged between every two adjacent connecting pieces.

[0042] It can be understood that in the present application, the first bearing 121 can be provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122, or the second bearing 123 can be provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122, or the first bearing 121 and the second bearing 123 can be provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122. The accompanying drawings of the present embodiment Figure 2 and the accompanying drawings Figure 6The second bearing 123 is provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122. In the drawings, Figure 2 and the drawings Figure 6 The grooves 126 are provided as five, and the annular grooves 127 are provided as two.

[0043] In the embodiment, the first bearing 121 and the second bearing 123 are provided to support the crankshaft 11, so that the crankshaft 11 in rotation does not produce torsion or deviation, effectively improving the accuracy and stability of the rotation of the crankshaft 11. At the same time, since at least one of the first bearing 121 and the second bearing 123 in the embodiment is provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122, this not only does not affect the sealing of the first bearing 121, the cylinder component 122 and the second bearing 123 after assembly, but also reduces the weight of at least one of the first bearing 121 and the second bearing 123, saves the raw material consumption required when manufacturing the first bearing 121 or the second bearing 123, thereby reducing the manufacturing cost and transportation cost of the compressor with the first bearing 121 and the second bearing 123, realizing the lightweight design and green energy-saving manufacturing of the compressor product, and having good social and economic value.

[0044] In addition, since the first bearing 121, the cylinder component 122 and the second bearing 123 in the embodiment are connected together through the connecting pieces, in order to reduce the weight of at least one of the first bearing 121 and the second bearing 123 while ensuring the structural strength of the compressor pump body 10, at least one groove 126 is provided between each adjacent two connecting pieces, so that not only installation space is provided for the connecting pieces, and the connection strength of the connecting pieces mounted on the compressor mechanism 12 is ensured, but also the total weight of at least one of the first bearing 121 and the second bearing 123 is reduced, thereby further reducing the overall weight of the compressor mechanism 12.

[0045] Further, the cylinder component 122 in the embodiment includes a cylinder body 1221 and a piston 1222, the crankshaft 11 has an eccentric portion 111, and the piston 1222 is sleeved on the eccentric portion 111 and located in the cylinder body 1221 to compress the refrigerant entering the cylinder component 122.

[0046] Further, referring to Figures 2 to 3 The second bearing 123 in the embodiment is provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122, each annular groove 127 is provided with a rib 129, and the rib 129 divides the annular groove 127 into a plurality of arc-shaped grooves; wherein the length L1 (as shown in the drawings) of the arc-shaped groove along the circumferential direction of the second bearing hole 125 is greater than the length L2 (as shown in the drawings) of the rib 129 along the circumferential direction of the second bearing hole 125. Figure 2L1 (as shown in Fig. 3) and the length L2 of the arc-shaped groove along the radial direction of the second bearing hole 125 (as shown in Fig. 3) satisfy the relationship: L1 > L2. Figure 2

[0047] Specifically, the second bearing 123 is provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder part 122, which not only does not affect the sealing performance of the second bearing 123 after being assembled with the cylinder part 122, but also reduces the weight of the second bearing 123. On this basis, the setting of the ribs 129 can improve the rigidity of the second bearing 123 after weight reduction, effectively guaranteeing the overall structural strength of the second bearing 123. At the same time, since the length L1 of the arc-shaped groove along the circumferential direction of the second bearing hole 125 is greater than the width L2 of the arc-shaped groove along the radial direction of the second bearing hole 125, the structure is simple and easy to process.

[0048] Further, the width D1 of the ribs 129 along the circumferential direction of the second bearing hole 125 (as shown in Fig. 3) in the embodiment satisfies the relationship 1mm≤D1≤10mm, for example, D1 can be set to 1mm, 2mm, 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, 10mm, etc.

[0049] Specifically, when D1 is less than 1mm, the width of the ribs 129 is narrow, and when the second bearing 123 bears external force, the ribs 129 are easily deformed or even broken, resulting in a decrease in the structural strength of the second bearing 123, and at the same time, the narrow width of the ribs 129 increases the processing difficulty; when D1 is greater than 10mm, the width of the ribs 129 is too wide, thereby occupying the space in the annular groove 127, which not only increases the material cost of the second bearing 123, but also increases the overall weight of the second bearing 123. That is to say, by making the width D1 of the ribs 129 along the circumferential direction of the second bearing hole 125 satisfy the relationship 1mm≤D1≤10mm in the embodiment, the weight of the second bearing 123 can be prevented from being too large on the premise of guaranteeing the structural strength of the second bearing 123.

[0050] ​Further, the number N of the ribs 129 in the embodiment satisfies the relationship: 3≤N≤8, for example, N can be set to 3, 4, 5, 6, 7, 8, etc. When N is less than 3, the ribs 129 are obviously insufficient in the separation and support of the annular groove 127 in the circumferential direction of the second bearing 123, which reduces the overall rigidity of the second bearing 123; when N is greater than 8, too many ribs 129 will cause the annular groove 127 to be excessively separated, resulting in a narrow space for each arc-shaped groove, and increasing the overall weight of the second bearing 123, thereby increasing the manufacturing cost and transportation cost of the compressor with the second bearing 123. That is to say, by making the number N of the ribs 129 satisfy the relationship: 3≤N≤8 in the embodiment, not only can the rigidity of the second bearing 123 be ensured, but also the weight of the second bearing 123 can be prevented from being too large. The embodiment of the annular groove 127 is shown in the following Figure 3 The case where the number of ribs 129 is 5 is shown in the following

[0051] Further, as shown in Figure 3 and Figure 6 , the second bearing 123 in the embodiment is provided with a plurality of grooves 126 and an annular groove 127 on the side away from the cylinder member 122, and the annular groove 127 includes a plurality of annular grooves 127, which are nested along the radial direction of the second bearing hole 125. It can be understood that the annular groove 127 in the embodiment can be provided with two, or three or more, and the embodiment of the annular groove 127 is shown in the following Figure 3 The case where the number of annular grooves 127 is two is shown in the following

[0052] Specifically, on the basis of providing one annular groove 127 on the side of the second bearing 123 away from the cylinder member 122, the provision of a plurality of annular grooves 127 can further reduce the overall weight of the second bearing 123, thereby reducing the manufacturing cost and transportation cost of the compressor with the second bearing 123. At the same time, since the plurality of annular grooves 127 in the embodiment are nested along the radial direction of the second bearing hole 125, in this way, during the operation of the compressor pump body 10, when the second bearing 123 is subjected to a radial force (such as centrifugal force, etc.) from the crankshaft 11, the nested annular grooves 127 can share and transmit the pressure layer by layer, thereby enhancing the radial bearing capacity of the second bearing 123, so that the second bearing 123 can more stably support the crankshaft 11.

[0053] Further, in order to make the weight of the second bearing 123 smaller and the manufacturing cost less, further reducing the waste of unnecessary materials, referring to Figures 3 to 4 and Figures 6 to 7As shown, the second bearing 123 in the embodiment is provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122, and each groove 126 extends in the radial direction of the second bearing hole 125 and penetrates the outer circumferential surface of the second bearing 123.

[0054] Specifically, the groove 126 in the embodiment is located at the outermost circle of the second bearing 123, and the groove 126 is in communication with the outer edge of the second bearing 123 to form a double-opening groove structure (i.e. a groove structure with two openings), so that the side of the groove 126 away from the second bearing hole 125 is not blocked by the groove wall, thereby further reducing the overall weight of the second bearing 123 without affecting the overall structural performance of the second bearing 123.

[0055] Further, referring to Figures 3 to 4 As shown, the second bearing 123 in the embodiment is provided with a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122, and the second bearing 123 is provided with a mounting hole 128 for the connecting member to pass through; wherein, along the axial direction of the second bearing hole 125, the maximum thickness H1 (as shown in Figure 5 As shown) between the annular groove 127 and the side of the second bearing 123 close to the cylinder component 122 and the thickness H2 (as shown in Figure 5 As shown) of the mounting hole 128 satisfies the relationship: 1.04≤H2 / H1≤1.39, for example, H2 / H1 can be set to 1.04, 1.1, 1.12, 1.14, 1.16, 1.18, 1.2, 1.22, 1.24, 1.26, 1.28, 1.3, 1.32, 1.34, 1.36, 1.38, 1.39, etc.

[0056] Specifically, when H2 / H1 is less than 1.04 and greater than or equal to 1, the values of H1 and H2 are relatively close, the axial thickness of the mounting hole 128 and the axial thickness of the second bearing 123 tend to be equal, and the weight reduction effect is poor; when H2 / H1 is less than 1, the axial thickness of the mounting hole 128 is relatively thin, and the maximum thickness between the annular groove 127 and the side of the second bearing 123 close to the cylinder component 122 is relatively thick, thereby causing the depth of the annular groove 127 in the axial direction of the second bearing hole 125 to be relatively deep, although the overall weight of the second bearing 123 can be reduced to a certain extent, the structural strength of the second bearing 123 near the annular groove 127 is weak and the rigidity is insufficient; when H2 / H1 is greater than 1.39, the maximum thickness between the annular groove 127 and the side of the second bearing 123 close to the cylinder component 122 is relatively thin, and the axial thickness of the mounting hole 128 is relatively thick, which may cause the structural strength of the side close to the annular groove 127 to be insufficient and the rigidity to be poor when the second bearing 123 bears axial force.

[0057] In other words, by making the value of H2 / H1 within the above range in this embodiment, not only can the overall thickness of the second bearing 123 be reduced by the annular groove 127, thereby reducing the consumption of raw materials required to manufacture the second bearing 123, but also the connection strength of the second bearing 123 after being connected to the cylinder component 122 through the mounting hole 128 is stronger, effectively improving the overall structural stability of the compressor pump body 10 during the rotation of the crankshaft 11.

[0058] Further, see Figures 3 to 4 As shown, in this embodiment, the second bearing 123 has a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122; wherein, along the axial direction of the second bearing hole 125, the maximum thickness H1 between the annular groove 127 and the side of the second bearing 123 near the cylinder component 122 (e.g., Figure 5 As shown) and the minimum thickness H3 between the annular groove 127 and the second bearing 123 near the cylinder component 122 (as shown) Figure 5 The relationship between H1 and H3 (as shown) is: 1.0≤H1 / H3≤1.4. For example, H1 / H3 can be set to 1.0, 1.05, 1.1, 1.15, 1.2, 1.25, 1.3, 1.35, 1.4, etc.

[0059] Specifically, when H1 / H3 is less than 1.0, the minimum thickness between the annular groove 127 and the side of the second bearing 123 near the cylinder component 122 is relatively large, resulting in a larger axial thickness of the second bearing 123 itself, increasing the overall weight of the second bearing 123 and thus increasing the consumption of raw materials required to manufacture the second bearing 123. When H1 / H3 is greater than 1.4, the maximum thickness between the annular groove 127 and the side of the second bearing 123 near the cylinder component 122 is relatively large, resulting in a deeper depth of the annular groove 127 along the axial direction of the second bearing hole 125. Although this can reduce the overall weight of the second bearing 123, the structural strength near the annular groove 127 on the second bearing 123 is weak and the rigidity is insufficient. That is to say, in this embodiment, by keeping H1 / H3 within the above range, not only can the thickness and weight of the second bearing 123 be reduced, but the structural strength of the second bearing 123 at the annular groove 127 can also be ensured.

[0060] Further, see Figures 3 to 4 As shown, in this embodiment, the second bearing 123 has a plurality of grooves 126 and at least one annular groove 127 on the side away from the cylinder component 122; wherein, along the axial direction of the second bearing hole 125, the maximum thickness H1 between the annular groove 127 and the side of the second bearing 123 near the cylinder component 122 (e.g., Figure 5the minimum thickness H4 (as shown) between the bottom of the groove 126 and the side of the second bearing 123 close to the cylinder member 122 satisfies the relationship: 1.0≤H1 / H4≤5.0, for example, H1 / H4 can be set to 1.0, 1.5, 2.0, 2.5, 3.0, 3.5, 4.0, 4.5, 5.0, etc. Figure 5

[0061] Specifically, when H1 / H4 is less than 1.0, the minimum thickness between the bottom of the groove 126 and the side of the second bearing 123 close to the cylinder member 122 is relatively thick, i.e., the axial depth of the groove 126 is shallow, thereby increasing the overall weight of the second bearing 123 and increasing the consumption of raw materials required for manufacturing the second bearing 123; when H1 / H4 is greater than 5.0, the maximum thickness between the annular groove 127 and the side of the second bearing 123 close to the cylinder member 122 is relatively thick, thereby causing the annular groove 127 to have a relatively deep axial depth along the second bearing hole 125, although the overall weight of the second bearing 123 can be reduced, the structural strength of the second bearing 123 near the annular groove 127 is weak and the rigidity is insufficient. That is to say, by making H1 / H4 within the above range in the present embodiment, not only can the weight of the second bearing 123 be effectively reduced, but also the structural strength of the thinnest part of the second bearing 123 can meet the connection strength requirement between the second bearing 123 and the cylinder member 122, effectively improving the fatigue resistance of the second bearing 123 and prolonging the service life of the second bearing 123.

[0062] Further, along the axial direction of the second bearing hole 125, the maximum thickness H1 (as shown) between the annular groove 127 and the side of the second bearing 123 close to the cylinder member 122 satisfies the relationship: 5.0mm≤H1≤6.6mm, for example, H1 can be set to 5.0mm, 5.2mm, 5.4mm, 5.6mm, 5.8mm, 6.0mm, 6.2mm, 6.4mm, 6.6mm, etc. Figure 5

[0063] Specifically, by making H1 within the above range in the present embodiment, the structural rigidity requirement of the second bearing 123 can be ensured while reducing the weight of the second bearing 123. When H1 is less than 5.0mm, the structural rigidity of the second bearing 123 cannot meet the requirement, thereby reducing the service life of the second bearing 123; when H1 is greater than 6.6mm, the weight reduction effect of the second bearing 123 is not obvious and the manufacturing cost cannot be effectively reduced.

[0064] Specifically, referring to Table 1 shown below, Table 1 shows the comparison between the weight of the second bearing 123 in the present application and that of the existing competitive products.

[0065] ​​Table 1 Comparison of the weight of the competitor bearing and the weight of the second bearing of the present application

[0066] Bearing type H1 / mm Weight / g Competitor bearing 7.0 170 Second bearing a1 6.6 123 Second bearing a2 5.0 112

[0067] As can be seen in Table 1, compared with the competitor bearing, the axial thickness H1 of the second bearing a1 and the second bearing a2 in the present embodiment is not greater than 6.6 mm, so that the weight of the second bearing a1 to the second bearing a2 is greatly reduced, and the smaller H1 is, the smaller the weight of the second bearing 123 is. It can be seen that under the condition that H1 satisfies the relationship: 5.0 mm≤H1≤6.6 mm, the weight reduction effect of the second bearing 123 is better.

[0068] Further, the sum V1 of the volumes of the plurality of grooves 126 and the at least one annular groove 127 in the present embodiment and the volume V of the first bearing 121 or the second bearing 123 satisfy the relationship: 0.15≤V1 / V≤0.35, for example, V1 / V can be set to 0.15, 0.17, 0.19, 0.20, 0.22, 0.04, 0.26, 0.28, 0.30, 0.32, 0.34, 0.35, etc.

[0069] Specifically, when V1 / V is less than 0.15, the volume occupied by the grooves 126 and the annular groove 127 is relatively small, thereby resulting in that the weight reduction effect of the first bearing 121 or the second bearing 123 is not obvious; when V1 / V is greater than 0.35, the volume occupied by the grooves 126 and the annular groove 127 is relatively large, thereby resulting in that the solid part of the first bearing 121 or the second bearing 123 is relatively small, and the overall structural strength of the first bearing 121 or the second bearing 123 is reduced.

[0070] Further, the sum V2 of the volumes of the plurality of annular grooves 127 in the present embodiment and the volume V of the first bearing 121 or the second bearing 123 satisfy the relationship: 0.0015≤V2 / V≤0.025, for example, V2 / V can be set to 0.0015, 0.002, 0.004, 0.006, 0.008, 0.010, 0.012, 0.014, 0.016, 0.018, 0.020, 0.022, 0.024, 0.025, etc.

[0071] Specifically, when V2 / V is less than 0.0015, the volume proportion of the annular groove 127 is too small, thereby resulting in that the weight reduction effect of the first bearing 121 or the second bearing 123 is not obvious; when V2 / V is greater than 0.025, the volume of the annular groove 127 is too large, thereby seriously weakening the solid structure strength of the first bearing 121 or the second bearing 123, and resulting in that the first bearing 121 or the second bearing 123 is deformed or even broken when bearing a huge radial force and an axial force.

[0072] Further, referring to Figure 3 and Figure 6 In the projection of the crankshaft 11 in the axial direction, the projection of the groove 126 in the embodiment includes at least one of a rectangle, a trapezoid, a circle, and a diamond. That is, the shape of the groove 126 in the embodiment can be one of a rectangle, a trapezoid, a circle, and a diamond, or at least two of a rectangle, a trapezoid, a circle, and a diamond. The specific structure can be set according to the actual processing conditions and requirements, and the present application does not make specific limitations.

[0073] The compressor pump body of the present application will be described in detail below in combination with specific embodiments.

[0074] Embodiment 1

[0075] Referring to Figure 2 and Table 2, the second bearing 123 in the embodiment is provided with a plurality of grooves 126 and two annular grooves 127 nested along the radial direction of the second bearing hole 125 on the side away from the cylinder part 122. Along the radial direction of the second bearing hole 125, each groove 126 extends in the direction away from the second bearing hole 125 and penetrates the outer peripheral surface of the second bearing 123, and at least one groove 126 is provided between each adjacent two connecting pieces. When H2 / H1 is equal to 1.04, the weight reduction effect of the second bearing 123 is weak, so that the rigidity of the second bearing 123 is strong. It is worth noting that the weak weight reduction effect of the second bearing 123 in the embodiment is relative to the weight reduction effect of the second bearing 123 when H2 / H1 is equal to 1.39. When H2 / H1 is equal to 1.04, not only can the second bearing 123 thin the overall thickness of the second bearing 123 through the annular groove 127 provided, so that the consumption of raw materials required for manufacturing the second bearing 123 is less, but also the connection strength of the second bearing 123 after being connected with the cylinder part 122 through the mounting hole 128 is stronger, effectively improving the stability of the overall structure of the compressor pump body 10 in the rotation process of the crankshaft 11.

[0076] Embodiment 2

[0077] Different from the embodiment 1, the H2 / H1 in the embodiment is equal to 1.39, so that the weight-reducing effect of the second bearing 123 is strong, and thus the rigidity of the second bearing 123 is weak. It is worth noting that the rigidity of the second bearing 123 in the embodiment is weak relative to the rigidity of the second bearing 123 when H2 / H1 is equal to 1.04. When H2 / H1 is equal to 1.39, not only can the second bearing 123 be thinned in overall thickness by the annular groove 127 provided, so that the consumption of raw materials required for manufacturing the second bearing 123 is less, but also the connection strength of the second bearing 123 after being connected with the cylinder member 122 through the mounting hole 128 is stronger, effectively improving the stability of the overall structure of the compressor pump body 10 during the rotation of the crankshaft 11.

[0078] Comparative Example 1

[0079] Different from the embodiment 1, the H2 / H1 in the embodiment is equal to 0.90, so that the weight-reducing effect of the second bearing 123 is too weak, and thus the rigidity of the second bearing 123 is too strong. Under the condition that H2 / H1 is equal to 0.90, it is difficult to thin the overall thickness of the second bearing 123, so that the consumption of raw materials required for manufacturing the second bearing 123 is more, and the manufacturing cost and the logistics transportation cost are increased.

[0080] Comparative Example 2

[0081] Different from the embodiment 1, the H2 / H1 in the embodiment is equal to 1.50, so that the weight-reducing effect of the second bearing 123 is too strong, and thus the rigidity of the second bearing 123 is too weak. Under the condition that H2 / H1 is equal to 1.50, it is difficult to ensure the overall structural strength of the second bearing 123, and under some heavy load working conditions, the second bearing 123 with insufficient rigidity can prematurely appear failure forms such as fatigue wear and plastic deformation, and the service life of the second bearing 123 is shortened.

[0082] Table 2 Influence of H2 / H1 on the Second Bearing

[0083]

[0084] It can be known from the above-mentioned examples and comparative examples that, by satisfying the relationship 1.04≤H2 / H1≤1.39 between the maximum thickness H1 between the annular groove 127 and the side of the second bearing 123 close to the cylinder member 122 and the thickness H2 of the mounting hole 128, not only can the overall thickness of the second bearing 123 be thinned by the annular groove 127, thereby reducing the consumption of raw materials for manufacturing the second bearing 123, but also the connection strength of the second bearing 123 after being connected with the cylinder member 122 through the mounting hole 128 is stronger, effectively improving the stability of the overall structure of the compressor pump body 10 during the rotation of the crankshaft 11.

[0085] Example 3

[0086] Referring to Figure 2 As shown in Table 3, the second bearing 123 in this example is provided with a plurality of grooves 126 and two annular grooves 127 nested along the radial direction of the second bearing hole 125 on the side of the second bearing 123 away from the cylinder member 122, and each groove 126 extends in the direction away from the second bearing hole 125 and penetrates the outer circumferential surface of the second bearing 123 along the radial direction of the second bearing hole 125. When H1 / H3 is equal to 1.0, the weight reduction effect of the second bearing 123 is weak, thereby making the rigidity of the second bearing 123 strong. It is worth noting that the weak weight reduction effect of the second bearing 123 in this example is relative to the weight reduction effect of the second bearing 123 when H1 / H3 is equal to 1.4. When H1 / H3 is equal to 1.0, not only can the thinning and weight reduction of the second bearing 123 be achieved, but also the structural strength of the second bearing 123 at the annular groove 127 can be ensured.

[0087] Example 4

[0088] Different from Example 3, H1 / H3 in this example is equal to 1.4, so that the weight reduction effect of the second bearing 123 is strong, thereby making the rigidity of the second bearing 123 weak. It is worth noting that the weak rigidity of the second bearing 123 in this example is relative to the rigidity of the second bearing 123 when H1 / H3 is equal to 1.0. When H1 / H3 is equal to 1.4, not only can the thinning and weight reduction of the second bearing 123 be achieved, but also the structural strength of the second bearing 123 at the annular groove 127 can be ensured.

[0089] Comparative Example 3

[0090] Different from the embodiment 3, the H1 / H3 in the present embodiment is equal to 0.9, thus, the weight of the second bearing 123 is increased, which results in that the rigidity of the second bearing 123 is too strong. Under the condition that the H1 / H3 is equal to 0.9, although the structural strength of the second bearing 123 can be ensured, it is difficult to realize the thinning and weight reduction of the second bearing 123, and the overall weight of the second bearing 123 is increased, thus, the consumption of raw materials required for manufacturing the second bearing 123 is increased.

[0091] Comparative example 4

[0092] Different from the embodiment 3, the H1 / H3 in the present embodiment is equal to 2.0, thus, the weight reduction effect of the second bearing 123 is too strong, which results in that the rigidity of the second bearing 123 is too weak. Under the condition that the H1 / H3 is equal to 2.0, although the overall weight of the second bearing 123 can be reduced, it is difficult to ensure the overall structural strength of the second bearing 123, and under some heavy load working conditions, the second bearing 123 with insufficient rigidity can prematurely appear failure forms such as fatigue wear and plastic deformation, which shortens the service life of the second bearing 123.

[0093] It can be known from the above-mentioned embodiments and comparative examples that, in the present application, by making the maximum thickness H1 between the annular groove 127 and the side of the second bearing 123 close to the cylinder member 122 and the minimum thickness H3 between the annular groove 127 and the side of the second bearing 123 close to the cylinder member 122 satisfy the relationship: 1.0≤H1 / H3≤1.4, not only the thinning and weight reduction of the second bearing 123 can be realized, but also the structural strength of the second bearing 123 at the annular groove 127 can be ensured.

[0094] Table 3 Influence of H1 / H3 on the second bearing

[0095]

[0096] Embodiment 5

[0097] Reference Figure 2As shown in Table 4, the second bearing 123 in the embodiment is provided with a plurality of grooves 126 and two annular grooves 127 nested along the radial direction of the second bearing hole 125 on the side away from the cylinder component 122. Each groove 126 extends towards the direction away from the second bearing hole 125 and penetrates the outer circumferential surface of the second bearing 123 along the radial direction of the second bearing hole 125. When H1 / H4 is equal to 1.0, the weight reduction effect of the second bearing 123 is weak, so that the rigidity of the second bearing 123 is strong. It is worth noting that the weak weight reduction effect of the second bearing 123 in the embodiment is relative to the weight reduction effect of the second bearing 123 when H1 / H4 is equal to 5.0. When H1 / H4 is equal to 1.0, not only can the weight reduction of the second bearing 123 be effectively realized, but also the structural strength of the thinnest part of the second bearing 123 can meet the connection strength requirement between the second bearing 123 and the cylinder component 122, effectively improve the fatigue resistance of the second bearing 123, and prolong the service life of the second bearing 123.

[0098] Example 6

[0099] Different from Example 5, H1 / H4 in the embodiment is equal to 5.0, so that the weight reduction effect of the second bearing 123 is strong, so that the rigidity of the second bearing 123 is weak. It is worth noting that the weak rigidity of the second bearing 123 in the embodiment is relative to the rigidity of the second bearing 123 when H1 / H4 is equal to 1.0. When H1 / H4 is equal to 5.0, not only can the weight reduction of the second bearing 123 be effectively realized, but also the structural strength of the thinnest part of the second bearing 123 can meet the connection strength requirement between the second bearing 123 and the cylinder component 122, effectively improve the fatigue resistance of the second bearing 123, and prolong the service life of the second bearing 123.

[0100] Comparative Example 5

[0101] Different from Example 5, H1 / H4 in the embodiment is equal to 0.9, so that the weight reduction of the second bearing 123 is too weak, so that the rigidity of the second bearing 123 is too strong. Under the condition that H1 / H4 is equal to 0.9, although the structural strength of the second bearing 123 can be ensured, the thinning and weight reduction of the second bearing 123 are difficult to realize, so that the overall weight of the second bearing 123 is increased, thereby increasing the consumption of raw materials required for manufacturing the second bearing 123.

[0102] Comparative Example 6

[0103] Different from the embodiment 5, the H1 / H4 in the present embodiment is equal to 5.5, thus, resulting in that the weight reduction of the second bearing 123 is too strong, thus resulting in that the rigidity of the second bearing 123 is too weak. Under the condition that the H1 / H4 is equal to 5.5, although the overall weight of the second bearing 123 can be reduced, it is difficult to guarantee the overall structural strength of the second bearing 123, and under certain heavy load working conditions, the second bearing 123 with insufficient rigidity can prematurely appear failure forms such as fatigue wear and plastic deformation, thereby shortening the service life of the second bearing 123.

[0104] It can be known from the above-mentioned embodiments and comparative examples that, in the present application, by satisfying the relationship: 1.0≤H1 / H4≤5.0 between the maximum thickness H1 between the annular groove 127 and the side of the second bearing 123 close to the cylinder member 122 and the minimum thickness H4 between the bottom of the groove 126 and the side of the second bearing 123 close to the cylinder member 122, not only can the weight reduction of the second bearing 123 be effectively realized, but also the structural strength of the thinnest part of the second bearing 123 can be ensured to meet the connection strength requirement between the second bearing 123 and the cylinder member 122, thereby effectively improving the fatigue resistance of the second bearing 123 and prolonging the service life of the second bearing 123.

[0105] Table 4 Influence of H1 / H4 on the second bearing

[0106]

[0107] On the other hand, referring to Figure 1 It is shown that the present application also provides a compressor, which comprises the compressor pump body 10 described above, and thus the compressor comprises all the technical effects of the compressor pump body 10 described above. Since the technical effects of the compressor pump body 10 have been described in detail in the foregoing, they will not be described here again.

[0108] Specifically, referring to Figure 1 It is shown that the compressor in the present embodiment comprises the compressor pump body 10, the shell 20 and the motor 30, the motor 30 and the compressor pump body 10 are both installed in the shell 20. Among them, the motor 30 comprises a stator 32 and a rotor 31, the rotor 31 is rotatably arranged in the stator 32 and connected with the end of the crankshaft 11 away from the compression mechanism 12, so as to drive the crankshaft 11 to rotate; the first bearing 121 in the compression mechanism 12 is connected with the inner peripheral wall of the shell 20.

[0109] Further, referring to Figure 1As shown, the compressor pump body 10 in the embodiment further comprises a silencer 13, which is arranged on the side of the first bearing 121 away from the cylinder component 122 and covers the exhaust hole (not shown in the figure) on the first bearing 121, and the silencer 13 is provided with an air outlet hole (not shown in the figure). After the compressed refrigerant is discharged from the exhaust hole, it can enter the silencer 13, and after being processed by the silencer 13, it is discharged into the shell 20, and finally discharged from the exhaust pipe 21 of the shell 20.

[0110] For the convenience of description, spatial relative terms such as "above", "upper", "top", "upper", etc. can be used herein to describe the spatial positional relationship of one device or feature with other devices or features as shown in the drawings. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation of the device described in the drawings. For example, if the device in the drawing is inverted, the device described as "above" or "above" other devices or structures will be positioned "below" or "below" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative description used herein is interpreted accordingly.

[0111] In addition, it should be noted that the use of "first", "second", etc. to define parts is only for the convenience of distinguishing the corresponding parts, and the above words have no special meaning unless otherwise stated, and therefore cannot be understood as limiting the scope of protection of the present application.

[0112] The above is only a preferred embodiment of the present application and is not intended to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included within the scope of protection of the present application.

Claims

1. A compressor pump body characterized by, Comprise: A crankshaft (11); A compression mechanism (12) comprising a first bearing (121), a cylinder member (122) and a second bearing (123), the first bearing (121), the cylinder member (122) and the second bearing (123) are sequentially sleeved on the crankshaft (11) along the axial direction of the crankshaft (11), the first bearing (121) has a first bearing hole (124) for the crankshaft (11) to pass through, the second bearing (123) has a second bearing hole (125) for the crankshaft (11) to pass through, at least one of the first bearing (121) and the second bearing (123) is provided with a plurality of grooves (126) and at least one annular groove (127) away from one side of the cylinder member (122), a plurality of the grooves (126) are arranged on the outer circumferential side of the first bearing (121) or the second bearing (123) along the circumferential direction of the first bearing hole (124) or the second bearing hole (125), and at least one annular groove (127) is arranged along the circumferential direction of the first bearing hole (124) or the second bearing hole (125). A plurality of connecting pieces are provided, the plurality of connecting pieces are arranged on the outer circumferential side of the compression mechanism (12) along the circumferential direction of the crankshaft (11) and sequentially pass through the first bearing (121), the cylinder member (122) and the second bearing (123), and at least one groove (126) is arranged between every two adjacent connecting pieces.

2. The compressor pump body of claim 1, wherein, The second bearing (123) is provided with a plurality of grooves (126) and at least one annular groove (127) away from one side of the cylinder member (122), each annular groove (127) is provided with a rib (129), and the rib (129) divides the annular groove (127) into a plurality of arc-shaped grooves; Wherein, the length L1 of the arc-shaped groove along the circumferential direction of the second bearing hole (125) and the width L2 of the arc-shaped groove along the radial direction of the second bearing hole (125) satisfy the relationship: L1>L2.

3. The compressor pump body of claim 2, wherein, The width D1 of the rib (129) along the circumferential direction of the second bearing hole (125) satisfies the relationship: 1mm≤D1≤10mm.

4. The compressor pump body of claim 2, wherein, The number N of the ribs (129) satisfies the relationship: 3≤N≤8.

5. The compressor pump body of claim 1, wherein, The second bearing (123) is provided with a plurality of grooves (126) and the annular groove (127) away from one side of the cylinder member (122), the annular groove (127) comprises a plurality of annular grooves (127), and the plurality of annular grooves (127) are nested along the radial direction of the second bearing hole (125); and / or, The second bearing (123) is provided with a plurality of grooves (126) and at least one annular groove (127) on the side away from the cylinder member (122), each of the grooves (126) extends in a direction away from the second bearing hole (125) and penetrates the outer circumferential surface of the second bearing (123) in the radial direction of the second bearing hole (125).

6. The compressor pump body of claim 1, wherein, The second bearing (123) is provided with a plurality of grooves (126) and at least one annular groove (127) on the side away from the cylinder member (122), and the second bearing (123) is provided with a mounting hole (128) through which the connecting member passes; Wherein, along the axial direction of the second bearing hole (125), the maximum thickness H1 between the annular groove (127) and the side of the second bearing (123) close to the cylinder member (122) and the thickness H2 of the mounting hole (128) satisfy the relationship: 1.04≤H2 / H1≤1.

39.

7. The compressor pump body of claim 1, wherein, The second bearing (123) is provided with a plurality of grooves (126) and at least one annular groove (127) on the side away from the cylinder member (122); Wherein, along the axial direction of the second bearing hole (125), the maximum thickness H1 between the annular groove (127) and the side of the second bearing (123) close to the cylinder member (122) and the minimum thickness H3 between the annular groove (127) and the side of the second bearing (123) close to the cylinder member (122) satisfy the relationship: 1.0≤H1 / H3≤1.

4.

8. The compressor pump body of claim 1, wherein, The second bearing (123) is provided with a plurality of grooves (126) and at least one annular groove (127) on the side away from the cylinder member (122); Wherein, along the axial direction of the second bearing hole (125), the maximum thickness H1 between the annular groove (127) and the side of the second bearing (123) close to the cylinder member (122) and the minimum thickness H4 between the bottom of the groove (126) and the side of the second bearing (123) close to the cylinder member (122) satisfy the relationship: 1.0≤H1 / H4≤5.

0.

9. The compressor pump body of any of claims 6-8, wherein, Along the axial direction of the second bearing hole (125), the maximum thickness H1 between the annular groove (127) and the side of the second bearing (123) close to the cylinder member (122) satisfies the relationship: 5.0mm≤H1≤6.6mm.

10. The compressor pump body of any one of claims 1-8, wherein, The sum V1 of the volumes of a plurality of grooves (126) and at least one annular groove (127) and the volume V of the first bearing (121) or the second bearing (123) satisfy the relationship: 0.15≤V1 / V≤0.35; and / or, The sum V2 of the volumes of a plurality of annular grooves (127) and the volume V of the first bearing (121) or the second bearing (123) satisfy the relationship: 0.0015≤V2 / V≤0.025; and / or, In a projection of the crankshaft (11) in the axial direction, the projection of the recess (126) comprises at least one of a rectangle, a trapezoid, a circle and a diamond.

11. A compressor characterized by, The compressor comprises the compressor pump body of any one of claims 1 to 10.

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