CN204140330U - For the compressing mechanism of compressor - Google Patents
For the compressing mechanism of compressor Download PDFInfo
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- CN204140330U CN204140330U CN201420542251.8U CN201420542251U CN204140330U CN 204140330 U CN204140330 U CN 204140330U CN 201420542251 U CN201420542251 U CN 201420542251U CN 204140330 U CN204140330 U CN 204140330U
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- valve plate
- exhaust valve
- head
- afterbody
- compressor
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Abstract
The utility model discloses a kind of compressing mechanism for compressor, comprising: bearing and exhaust valve plate.Bearing is provided with exhaust port.The joint that exhaust valve plate has head, afterbody and is connected between head and afterbody, afterbody is fixed on bearing, head coordinates to open or close exhaust port with exhaust port, wherein, the thickness of exhaust valve plate is T, and the distance between the immovable point of afterbody and bearing and the center of exhaust port is L, and the width of joint is b0, T, L and b0 meet relation: T/b0≤0.045, b0/L >=0.12.According to the compressing mechanism for compressor of the present utility model, by limiting exhaust valve plate size, thus reducing the exhaust resistance of exhaust valve plate, improving compressor performance, reduce the torsional deformation of exhaust valve plate under exhaust airstream impacts simultaneously, improve the noise level of compressor.And exhaust valve plate structure is simple, with low cost, easy to manufacture, be widely used.
Description
Technical field
The utility model relates to compressor field, especially relates to a kind of compressing mechanism for compressor.
Background technique
For meeting power conservation requirement, the efficiency requirements of people to compressor is more and more higher.For improving compressor efficiency, reduce compressor power consumption, the exhaust resistance of compressor can suitably reduce.
The method reducing the exhaust resistance of compressor has multiple, and wherein a kind of is adjust the thickness of exhaust valve plate, effectively to reduce the exhaust resistance of exhaust valve plate, reaches the object improving compressor compresses performance.But the thickness of exhaust valve plate can cause the reduced stiffness of exhaust valve plate after reducing, under the impact of exhaust airstream, outlet valve sector-meeting is distorted distortion, and exhaust valve plate pats the noise that valve seat produces to be increased, and affects the comfort level of user's use.
Model utility content
The utility model is intended at least solve the technical problem existed in prior art.For this reason, the purpose of this utility model is to provide a kind of compressing mechanism for compressor, and this compressing mechanism can reduce exhaust resistance, reduces noise simultaneously.
According to the compressing mechanism for compressor of the utility model first embodiment, comprising: bearing, described bearing is provided with exhaust port; Exhaust valve plate, the joint that described exhaust valve plate has head, afterbody and is connected between described head and described afterbody, described afterbody is fixed on described bearing, described head coordinates to open or close described exhaust port with described exhaust port, wherein, the thickness of described exhaust valve plate is T, distance between the immovable point of described afterbody and described bearing and the center of described exhaust port is L, the width of described joint is b0, described T, L and b0 meet relation: T/b0≤0.045, b0/L >=0.12.
According to the compressing mechanism for compressor of the utility model first embodiment, by limiting the thickness of exhaust valve plate and the width of linkage section, thus reduce the exhaust resistance of exhaust valve plate, improve compressor performance, reduce the torsional deformation of exhaust valve plate under exhaust airstream impacts simultaneously, improve the noise level of compressor.And exhaust valve plate structure is simple, with low cost, easy to manufacture, be widely used.
Particularly, described head is formed as circular.Thus make nose shape simple, easily process.
More specifically, when described head closes described exhaust port, the center of circle of described head and the center of circle of described exhaust port are positioned on same vertical curve.Thus ensure that the outward edge of head and the outward edge of exhaust port are apart from even, and then during guarantee head closedown exhaust port, exhaust port not easily leaks gas.
Alternatively, described afterbody comprises: square plate, and described side's plate is connected with described joint; Semi-circular plate, described semi-circular plate extends from one end away from described joint of described side's plate towards the direction away from described joint.
According to the compressing mechanism for compressor of the utility model second embodiment, comprising: bearing, described bearing is provided with exhaust port, exhaust valve plate, described exhaust valve plate has head, afterbody and the joint be connected between described head and described afterbody, described afterbody is fixed on described bearing, described head coordinates to open or close described exhaust port with described exhaust port, described joint comprises connected first paragraph and second segment, the width of described first paragraph is less than the width of described second segment, described first paragraph is connected with described head, described second segment is connected with described afterbody, the thickness of described exhaust valve plate is T, distance between the immovable point of described afterbody and described bearing and the center of described exhaust port is L, the width of described first paragraph is b1 and length is m1, the width of described second segment is b2 and length is m2, wherein, described T, L and b1 meets relation: T/b1≤0.045, b1/L >=0.12, or as T/b1>0.045, described T, L, m1, b2 and m2 meet relation: T/b2≤0.045, b2/L >=0.12 and m1/m2≤3.
According to the compressing mechanism for compressor of the utility model second embodiment, by limiting the width of the width of the thickness of exhaust valve plate, the first paragraph of linkage section and length, second segment and length, thus reduce the exhaust resistance of exhaust valve plate, improve compressor performance, reduce the torsional deformation of exhaust valve plate under exhaust airstream impacts simultaneously, improve the noise level of compressor.And exhaust valve plate structure is simple, with low cost, easy to manufacture, be widely used.
Particularly, described head is formed as circular.Thus make nose shape simple, easily process.
More specifically, when described head closes described exhaust port, the center of circle of described head and the center of circle of described exhaust port are positioned on same vertical curve.Thus ensure that the outward edge of head and the outward edge of exhaust port are apart from even, and then during guarantee head closedown exhaust port, exhaust port not easily leaks gas.
Alternatively, described afterbody comprises: square plate, and described side's plate is connected with described joint; Semi-circular plate, described semi-circular plate extends from one end away from described joint of described side's plate towards the direction away from described joint.
Additional aspect of the present utility model and advantage will part provide in the following description, and part will become obvious from the following description, or be recognized by practice of the present utility model.
Accompanying drawing explanation
Above-mentioned and/or additional aspect of the present utility model and advantage will become obvious and easy understand from accompanying drawing below combining to the description of embodiment, wherein:
Fig. 1 is the structural representation of the exhaust valve plate according to the utility model first embodiment, wherein, and the plan view that (a) is this exhaust valve plate, the plan view that (b) is this exhaust valve plate;
Fig. 2 is the structural representation of the exhaust valve plate according to the utility model second embodiment, wherein, and the plan view that (c) is this exhaust valve plate, the plan view that (d) is this exhaust valve plate;
Fig. 3 is the ratio relation figure of compressor performance COP value according to the utility model embodiment and T/b0 (T/b1, T/b2);
Fig. 4 is the ratio relation figure of compressor noise amount according to the utility model embodiment and b0/L (b1/L, b2/L).
Reference character:
Exhaust valve plate 100, head 1, afterbody 2, square plate 21, semi-circular plate 22, joint 3, first paragraph 31, second segment 32, attachment hole 4.
Embodiment
Be described below in detail embodiment of the present utility model, the example of described embodiment is shown in the drawings, and wherein same or similar label represents same or similar element or has element that is identical or similar functions from start to finish.Be exemplary below by the embodiment be described with reference to the drawings, be intended to for explaining the utility model, and can not be interpreted as restriction of the present utility model.
In description of the present utility model, it will be appreciated that, term " " center ", " length ", " width ", " thickness ", " on ", D score, " front ", " afterwards ", " left side ", " right side ", " vertically ", " level ", orientation or the position relationship of the instruction such as " radial direction " are based on orientation shown in the drawings or position relationship, only the utility model and simplified characterization for convenience of description, instead of indicate or imply that the device of indication or element must have specific orientation, with specific azimuth configuration and operation, therefore can not be interpreted as restriction of the present utility model.
In addition, term " first ", " second " only for describing object, and can not be interpreted as instruction or hint relative importance or imply the quantity indicating indicated technical characteristics.Thus, be limited with " first ", the feature of " second " can express or impliedly comprise one or more these features.In description of the present utility model, except as otherwise noted, the implication of " multiple " is two or more.
In description of the present utility model, unless otherwise clearly defined and limited, term " is connected ", " connection ", " fixing " should be interpreted broadly, and such as, can be fixedly connected with, also can be removably connect, or integral; It can be mechanical connection; Can be directly be connected.For the ordinary skill in the art, concrete condition the concrete meaning of above-mentioned term in the utility model can be understood.
For meeting power conservation requirement, the efficiency requirements of people to compressor is more and more higher.For improving compressor efficiency, reduce compressor power consumption, the exhaust resistance of compressor can suitably reduce.For this reason, the utility model proposes a kind of compressing mechanism for compressor, and the size of the exhaust valve plate 100 of compressing mechanism is limited.And, the utility model embodiment proposes the exhaust valve plate 100 of two kinds of structures, these two kinds of exhaust valve plates 100 are tested by model utility people respectively, and sum up, analyze the optimal size scope of exhaust valve plate 100 according to test result, to improving the noise condition of compressor while reduction compressor air-discharging resistance.
The compressing mechanism being used for compressor according to the utility model first embodiment is described below with reference to Fig. 1, Fig. 3 and Fig. 4.
According to the compressing mechanism for compressor of the utility model first embodiment, compressing mechanism comprises bearing (scheming not shown) and exhaust valve plate 100, and bearing is provided with exhaust port.
With reference to Fig. 1, the joint 3 that exhaust valve plate 100 has head 1, afterbody 2 and is connected between head 1 and afterbody 2, afterbody 2 is fixed on bearing, and head 1 coordinates to open or close exhaust port with exhaust port.
It should be noted that, compressing mechanism also comprises the valve seat (scheming not shown) of annular, and valve seat to be located on bearing and to arrange around exhaust port.Because exhaust valve plate 100 is fixed on bearing by afterbody 2, therefore in its natural state, the head 1 of exhaust valve plate 100 covers on valve seat, thus realize the closedown of exhaust port, after compressing mechanism has compressed gas, exhaust airstream in compressing mechanism can impact the head 1 of exhaust valve plate 100 from exhaust port, thus realizes opening of exhaust port.
With reference to Fig. 1, exhaust valve plate 100 is substantially plate shaped, and the thickness of exhaust valve plate 100 is T, and the distance between the immovable point of afterbody 2 and bearing and the center of exhaust port is L." thickness " refers to the size of parts on above-below direction.
In first embodiment, the shape of head 1 does not do concrete restriction, as long as head 1 can cover valve seat completely, such as head 1 can be formed as oval or irregularly shaped, and and for example shown in Fig. 1 (b), head 1 is formed as circular, thus make head 1 simple shape, easily process.When head 1 closes exhaust port, the center of circle of head 1 and the center of circle of exhaust port are positioned on same vertical curve, namely when head 1 closes exhaust port, head 1 is arranged with exhaust port is concentric, thus the outward edge distance ensureing outward edge and the exhaust port of head 1 evenly, and then when guarantee head 1 closes exhaust port, exhaust port not easily leaks gas.
Here, the shape of afterbody 2 does not do concrete restriction yet, as afterbody 2 can be formed as circular or irregularly shaped, and for example shown in Fig. 1 (b), afterbody 2 side of comprising plate 21 and semi-circular plate 22, side's plate 21 is connected with joint 3, and semi-circular plate 22 extends from one end away from joint 3 of square plate 21 towards the direction away from joint 3.In addition, afterbody 2 does not do concrete restriction with the means of fixation of bearing yet, as in Fig. 1 (b) example shown, afterbody 2 is provided with attachment hole 4 through in the vertical direction, afterbody 2 is fixed on bearing by the fixed block through attachment hole 4, wherein, fixed block can be rivet, and namely exhaust valve plate 100 is riveted on bearing.
Therefore in the example depicted in fig. 1, the immovable point of afterbody 2 and bearing is concentric with the attachment hole 4 on afterbody 2, and head 1 is concentric with the exhaust port of bearing, therefore, when head 1 closes exhaust port, the distance between the center of the attachment hole 4 on exhaust valve plate 100 and the center of head 1 equals L.
With reference to Fig. 1, in a first embodiment, the head 1 of exhaust valve plate 100 adopts one-part form to be connected with between afterbody 2, and namely the width of joint 3 is unanimous on the whole, and therefore the width of joint 3 can be set as b0.Here, " width " refers to the size of parts on fore-and-aft direction.
In a first embodiment, verified from the many experiments of model utility people, when T, L and b0 meet relation: T/b0≤0.045, during b0/L >=0.12, greatly can reduce the exhaust resistance of compressor, reduce the noise of compressor simultaneously.
Specifically, the compressor in the first embodiment has been carried out testing property by model utility people, and simulates the ratio of T/b0 and the graph of a relation of compressor performance COP value, as shown in Figure 3.As shown in Figure 3, COP value reduces along with the increase of the ratio of T/b0, therefore, when the width b0 of joint 3 is certain, by reducing the thickness T of exhaust valve plate 100, can reach the object reducing exhaust resistance, improve compressor performance.And as shown in Figure 3, when T/b0≤0.045, compressor performance COP value is higher, the increase of the ratio as T/b0>0.045 and along with T/b0, compressor performance COP value sharply declines.Therefore, in a first embodiment, when the size of exhaust valve plate 100 meets T/b0≤0.045, can ensure that the exhaust resistance of exhaust valve plate 100 is less, compressor performance is higher.
When thickness T due to exhaust valve plate 100 reduces, the reduced stiffness of exhaust valve plate 100, therefore need to strengthen the width b0 of joint 3, guarantee that exhaust valve plate 100 can not be distorted distortion under the impact of exhaust airstream, thus the noise produced when suppression exhaust valve plate 100 pats valve seat.For this reason, the compressor in the first embodiment has been carried out noise test by model utility people, and simulates the ratio of b0/L and the graph of a relation of compressor noise amount, as shown in Figure 4.Wherein, compressor noise amount reduces along with the increase of the ratio of b0/L, and when b0/L >=0.12, compressor noise amount remains in lower scope.Therefore in a first embodiment, when the size of exhaust valve plate 100 meets b0/L >=0.12, the torsional deformation of exhaust valve plate 100 under exhaust airstream impacts can be reduced, ensure that exhaust valve plate 100 steadily can be opened and close under exhaust airstream impacts, thus reduce the noise sent when exhaust valve plate 100 uses, improve the noise level of compressor.
In addition, because the utility model first embodiment does not propose concrete restriction to the head 1 of exhaust valve plate 100 and the shape of afterbody 2, and only size restriction is proposed to the thickness T of exhaust valve plate 100, the width b0 of joint 3, therefore the exhaust valve plate 100 of the first embodiment is provided with structure simply, the advantage that cost is low, manufacture is simple and operation strategies is wide.
According to the compressing mechanism for compressor of the utility model first embodiment, by limiting the thickness T of the exhaust valve plate 100 and width b0 of linkage section 3, thus reduce the exhaust resistance of exhaust valve plate 100, improve compressor performance, reduce the torsional deformation of exhaust valve plate 100 under exhaust airstream impacts simultaneously, improve the noise level of compressor.And exhaust valve plate 100 structure is simple, with low cost, easy to manufacture, be widely used.
The compressing mechanism being used for compressor according to the utility model second embodiment is described below with reference to Fig. 2, Fig. 3 and Fig. 4.
According to the compressing mechanism for compressor of the utility model second embodiment, compressing mechanism comprises bearing (scheming not shown) and exhaust valve plate 100, and bearing is provided with exhaust port.
With reference to Fig. 2, the joint 3 that exhaust valve plate 100 has head 1, afterbody 2 and is connected between head 1 and afterbody 2, afterbody 2 is fixed on bearing, and head 1 coordinates to open or close exhaust port with exhaust port.In a second embodiment, the working method of exhaust valve plate 100 is identical with the working method of exhaust valve plate 100 in the first embodiment, no longer describes here.
Wherein, exhaust valve plate 100 is substantially plate shaped, and the thickness of exhaust valve plate 100 is T, and the distance between the immovable point of afterbody 2 and bearing and the center of exhaust port is L.
In second embodiment, the shape of head 1 does not do concrete restriction, as long as head 1 can cover valve seat completely, such as head 1 can be formed as oval or irregularly shaped, and and for example shown in Fig. 2 (d), head 1 is formed as circular, thus make head 1 simple shape, easily process.When head 1 closes exhaust port, the center of circle of head 1 and the center of circle of exhaust port are positioned on same vertical curve, namely when head 1 closes exhaust port, head 1 is arranged with exhaust port is concentric, thus the outward edge distance ensureing outward edge and the exhaust port of head 1 evenly, and then when guarantee head 1 closes exhaust port, exhaust port not easily leaks gas.
And, the shape of afterbody 2 does not do concrete restriction yet, as afterbody 2 can be formed as circular or irregularly shaped, and for example shown in Fig. 2 (d), afterbody 2 side of comprising plate 21 and semi-circular plate 22, side's plate 21 is connected with joint 3, and semi-circular plate 22 extends from one end away from joint 3 of square plate 21 towards the direction away from joint 3.In addition, afterbody 2 does not do concrete restriction with the means of fixation of bearing yet, as in Fig. 2 (d) example shown, afterbody 2 is provided with attachment hole 4 through in the vertical direction, afterbody 2 is fixed on bearing by the fixed block through attachment hole 4, wherein, fixed block can be rivet, and namely exhaust valve plate 100 is riveted on bearing.
Therefore in the illustrated example shown in fig. 2, the immovable point of afterbody 2 and bearing is concentric with the attachment hole 4 on afterbody 2, and head 1 is concentric with the exhaust port of bearing, therefore, when head 1 closes exhaust port, the distance between the center of the attachment hole 4 on exhaust valve plate 100 and the center of head 1 equals L.
With reference to Fig. 2, in a second embodiment, the head 1 of exhaust valve plate 100 adopts two-part to be connected with between afterbody 2, namely joint 3 comprises connected first paragraph 31 and second segment 32, the width of first paragraph 31 is less than the width of second segment 32, and first paragraph 31 is connected with head 1, and second segment 32 is connected with afterbody 2.The width of first paragraph 31 is b1 and length is m1, and the width of second segment 32 is b2 and length is m2.
In a second embodiment, verified, when T, L and b1 meet relation from the many experiments of model utility people: T/b1≤0.045 and b1/L >=0.12 time, greatly can reduce the exhaust resistance of compressor, reduce the noise of compressor simultaneously.
Specifically, the compressor in the second embodiment has been carried out testing property by model utility people, and simulates the ratio of T/b1 and the graph of a relation of compressor performance COP value, as shown in Figure 3.As shown in Figure 3, COP value reduces, therefore, when the width b1 of the first paragraph 31 of joint 3 is certain along with the increase of the ratio of T/b1, by reducing the thickness T of exhaust valve plate 100, the object reducing exhaust resistance, improve compressor performance can be reached.And as shown in Figure 3, when T/b1≤0.045, compressor performance COP value is higher, the increase of the ratio as T/b1>0.045 and along with T/b1, compressor performance COP value sharply declines.Therefore in a second embodiment, the size of exhaust valve plate 100 need meet T/b1≤0.045, and can ensure that the exhaust resistance of exhaust valve plate 100 is less, compressor performance is higher.
When the thickness T of exhaust valve plate 100 reduces, the reduced stiffness of exhaust valve plate 100, therefore the width b1 of the first paragraph 31 strengthening joint 3 is needed, guarantee that exhaust valve plate 100 can not be distorted distortion under the impact of exhaust airstream, thus the noise produced when suppressing exhaust valve plate 100 to pat valve seat.For this reason, the compressor in the second embodiment has been carried out noise test by model utility people, and simulates the ratio of b1/L and the graph of a relation of compressor noise amount, as shown in Figure 4.Wherein, when b1/L >=0.12, compressor noise amount remains in lower scope.Therefore in a second embodiment, the size of exhaust valve plate 100 meets b1/L >=0.12, the torsional deformation of exhaust valve plate 100 under exhaust airstream impacts can be reduced, ensure that exhaust valve plate 100 steadily can be opened and close under exhaust airstream impacts, thus reduce the noise sent when exhaust valve plate 100 uses, improve the noise level of compressor.
In a second embodiment, as T/b1>0.045, T, L, m1, b2 and m2 meet relation: T/b2≤0.045, b2/L >=0.12 and m1/m2≤3, also greatly can reduce the exhaust resistance of compressor, reduce the noise of compressor simultaneously.
Here, situation in second embodiment during T/b1>0.045 has also been carried out compressor performance test by model utility people, wherein, when m1/m2≤3, model utility human simulation has gone out the ratio of T/b2 and the graph of a relation of compressor performance COP value, as shown in Figure 3.Wherein, COP value reduces along with the increase of the ratio of T/b2, and when T/b2≤0.045, compressor performance COP value is higher, the increase of the ratio as T/b2>0.045 and along with T/b2, and compressor performance COP value sharply declines.Therefore, in a second embodiment, as T/b1>0.045, the size of exhaust valve plate 100 meets T/b2≤0.045, and m1/m2≤3, can ensure that the exhaust resistance of exhaust valve plate 100 is less, compressor performance is higher.
And as T/b1>0.045 and m1/m2≤3 time, model utility people has also simulated the ratio of b2/L and the graph of a relation of compressor noise amount according to noise experimental result, as shown in Figure 4.Wherein, when b2/L >=0.12, compressor noise amount remains in lower scope.Therefore in a second embodiment, as T/b1>0.045, the size of exhaust valve plate 100 meets b2/L >=0.12 and m1/m2≤3, also the torsional deformation of exhaust valve plate 100 under exhaust airstream impacts can be reduced, ensure that exhaust valve plate 100 steadily can be opened and close under exhaust airstream impacts, thus reduce the noise sent when exhaust valve plate 100 uses, improve the noise level of compressor.
In addition, because the utility model second embodiment does not propose concrete restriction to the head 1 of exhaust valve plate 100 and the shape of afterbody 2, and only size is proposed to the width b2 of the width b1 of the thickness T of exhaust valve plate 100, the first paragraph 31 of joint 3 and length m1, second segment 32 and length m2 and limit, therefore the exhaust valve plate 100 of the second embodiment is also provided with structure simply, the advantage that cost is low, manufacture is simple and operation strategies is wide.
According to the compressing mechanism for compressor of the utility model second embodiment, by limiting the width b2 of the width b1 of the thickness T of exhaust valve plate 100, the first paragraph 31 of linkage section 3 and length m1, second segment 32 and length m2, thus reduce the exhaust resistance of exhaust valve plate 100, improve compressor performance, reduce the torsional deformation of exhaust valve plate 100 under exhaust airstream impacts simultaneously, improve the noise level of compressor.And exhaust valve plate 100 structure is simple, with low cost, easy to manufacture, be widely used.
In the description of this specification, specific features, structure, material or feature that the description of reference term " embodiment ", " some embodiments ", " example ", " concrete example " or " some examples " etc. means to describe in conjunction with this embodiment or example are contained at least one embodiment of the present utility model or example.In this manual, identical embodiment or example are not necessarily referred to the schematic representation of above-mentioned term.And the specific features of description, structure, material or feature can combine in an appropriate manner in any one or more embodiment or example.
Although illustrate and described embodiment of the present utility model, those having ordinary skill in the art will appreciate that: can carry out multiple change, amendment, replacement and modification to these embodiments when not departing from principle of the present utility model and aim, scope of the present utility model is by claim and equivalents thereof.
Claims (8)
1. for a compressing mechanism for compressor, it is characterized in that, comprising:
Bearing, described bearing is provided with exhaust port;
Exhaust valve plate, the joint that described exhaust valve plate has head, afterbody and is connected between described head and described afterbody, described afterbody is fixed on described bearing, described head coordinates to open or close described exhaust port with described exhaust port, wherein, the thickness of described exhaust valve plate is T, and the distance between the immovable point of described afterbody and described bearing and the center of described exhaust port is L, the width of described joint is b0, and described T, L and b0 meet relation:
T/b0≤0.045，b0/L≥0.12。
2. the compressing mechanism for compressor according to claim 1, is characterized in that, described head is formed as circular.
3. the compressing mechanism for compressor according to claim 2, is characterized in that, when described head closes described exhaust port, the center of circle of described head and the center of circle of described exhaust port are positioned on same vertical curve.
4. the compressing mechanism for compressor according to claim 1, is characterized in that, described afterbody comprises:
Side's plate, described side's plate is connected with described joint;
Semi-circular plate, described semi-circular plate extends from one end away from described joint of described side's plate towards the direction away from described joint.
5. for a compressing mechanism for compressor, it is characterized in that, comprising:
Bearing, described bearing is provided with exhaust port;
Exhaust valve plate, described exhaust valve plate has head, afterbody and the joint be connected between described head and described afterbody, described afterbody is fixed on described bearing, described head coordinates to open or close described exhaust port with described exhaust port, described joint comprises connected first paragraph and second segment, the width of described first paragraph is less than the width of described second segment, described first paragraph is connected with described head, described second segment is connected with described afterbody, the thickness of described exhaust valve plate is T, distance between the immovable point of described afterbody and described bearing and the center of described exhaust port is L, the width of described first paragraph is b1 and length is m1, the width of described second segment is b2 and length is m2, wherein,
Described T, L and b1 meet relation: T/b1≤0.045, b1/L >=0.12; Or
As T/b1>0.045, described T, L, m1, b2 and m2 meet relation: T/b2≤0.045, b2/L >=0.12 and m1/m2≤3.
6. the compressing mechanism for compressor according to claim 5, is characterized in that, described head is formed as circular.
7. the compressing mechanism for compressor according to claim 6, is characterized in that, when described head closes described exhaust port, the center of circle of described head and the center of circle of described exhaust port are positioned on same vertical curve.
8. the compressing mechanism for compressor according to claim 5, is characterized in that, described afterbody comprises:
Side's plate, described side's plate is connected with described joint;
Semi-circular plate, described semi-circular plate extends from one end away from described joint of described side's plate towards the direction away from described joint.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420542251.8U CN204140330U (en) | 2014-09-19 | 2014-09-19 | For the compressing mechanism of compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420542251.8U CN204140330U (en) | 2014-09-19 | 2014-09-19 | For the compressing mechanism of compressor |
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| CN204140330U true CN204140330U (en) | 2015-02-04 |
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| CN201420542251.8U Withdrawn - After Issue CN204140330U (en) | 2014-09-19 | 2014-09-19 | For the compressing mechanism of compressor |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104989627A (en) * | 2015-07-23 | 2015-10-21 | 珠海凌达压缩机有限公司 | Compressor and flapper valve block thereof |
| CN105484975A (en) * | 2014-09-19 | 2016-04-13 | 广东美芝制冷设备有限公司 | Compressing mechanism for compressor |
| CN106194667A (en) * | 2015-04-30 | 2016-12-07 | 江苏白雪电器股份有限公司 | Carbon-dioxide gas compressor valve block and manufacture method thereof |
| CN106930949A (en) * | 2015-12-30 | 2017-07-07 | 珠海格力节能环保制冷技术研究中心有限公司 | Exhaust valve plate component, flange assembly and compressor |
| CN109139426A (en) * | 2018-11-07 | 2019-01-04 | 韶关市立全机械有限公司 | A kind of compressor valve plate with shock resistance reseting performance |
| CN109139426B (en) * | 2018-11-07 | 2024-04-19 | 广东立全智造阀片有限公司 | Compressor valve block with impact resistance reset performance |
-
2014
- 2014-09-19 CN CN201420542251.8U patent/CN204140330U/en not_active Withdrawn - After Issue
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105484975A (en) * | 2014-09-19 | 2016-04-13 | 广东美芝制冷设备有限公司 | Compressing mechanism for compressor |
| CN105484975B (en) * | 2014-09-19 | 2018-09-28 | 广东美芝制冷设备有限公司 | Compression mechanism for compressor |
| CN106194667A (en) * | 2015-04-30 | 2016-12-07 | 江苏白雪电器股份有限公司 | Carbon-dioxide gas compressor valve block and manufacture method thereof |
| CN104989627A (en) * | 2015-07-23 | 2015-10-21 | 珠海凌达压缩机有限公司 | Compressor and flapper valve block thereof |
| CN106930949A (en) * | 2015-12-30 | 2017-07-07 | 珠海格力节能环保制冷技术研究中心有限公司 | Exhaust valve plate component, flange assembly and compressor |
| CN109139426A (en) * | 2018-11-07 | 2019-01-04 | 韶关市立全机械有限公司 | A kind of compressor valve plate with shock resistance reseting performance |
| CN109139426B (en) * | 2018-11-07 | 2024-04-19 | 广东立全智造阀片有限公司 | Compressor valve block with impact resistance reset performance |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20150204 Effective date of abandoning: 20180928 |
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| AV01 | Patent right actively abandoned |