WO2017084133A1 - Structure de raccordement sûre pour culasse et plaque de siège de soupape de compresseur d'air - Google Patents

Structure de raccordement sûre pour culasse et plaque de siège de soupape de compresseur d'air Download PDF

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Publication number
WO2017084133A1
WO2017084133A1 PCT/CN2015/097273 CN2015097273W WO2017084133A1 WO 2017084133 A1 WO2017084133 A1 WO 2017084133A1 CN 2015097273 W CN2015097273 W CN 2015097273W WO 2017084133 A1 WO2017084133 A1 WO 2017084133A1
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WIPO (PCT)
Prior art keywords
cylinder
seat plate
valve seat
main bearing
head
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PCT/CN2015/097273
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English (en)
Chinese (zh)
Inventor
耿爱农
陈威龙
阮勤江
陈君立
Original Assignee
浙江鸿友压缩机制造有限公司
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Publication of WO2017084133A1 publication Critical patent/WO2017084133A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections

Definitions

  • the invention belongs to the technical field of compressors, and relates to a fastening connection structure of a cylinder head and a valve seat plate of an air compressor, in particular to a quick and reliable fastening connection of an air compressor cylinder head and a valve seat plate.
  • the structure to the main bearing housing.
  • the existing air compressor mainly has driving motor, main bearing, main bearing seat, crankshaft, connecting rod, piston, cylinder, valve seat plate and cylinder head, etc., wherein the crankshaft is supported by the main bearing on the main bearing housing and is driven by the motor. Rotating the drive, the piston is mounted in the cylinder and driven by the crankshaft through the connecting rod to reciprocate relative to the cylinder, and the cylinder head and the valve seat plate are fastened to the main bearing housing by bolts and by the cylinder head or The valve seat plate also presses the cylinder against the main bearing housing.
  • Conventional compressors generally use not less than four bolts to fasten the cylinder head and the valve seat plate to the main bearing housing. The consideration is that the spacing between the bolts can be made smaller to ensure the cylinder.
  • too many bolts tend to cause an increase in the manufacturing cost of the compressor, on the one hand, the number of machining times and time, and the other On the one hand, increased workers The installation and inspection workload; 4) too many bolts can easily lead to increased volume and waste of materials in the compressor. Due to the large number of bolts to be installed, the main bearing housing must be made into a space frame or even a crankcase. The structure, in this way, not only has a large space and consumes a lot of materials. In summary, the traditional use of four and more than four bolts to tighten the cylinder head and the seat plate to the main bearing seat is undoubtedly there is room for improvement, at least for large and medium-sized displacement air compression Machine is a fact that does exist.
  • the present invention proposes a fastening connection structure of the air compressor cylinder head and the valve seat plate. It is: by reducing the number of bolts that fasten the cylinder head and the valve seat plate to the main bearing seat, thereby improving the consistency of the bolt fastening degree, improving the working reliability of the compressor, and reducing the manufacturing cost of the compressor, Reduce the material used to make the compressor.
  • the object of the present invention is to achieve a fastening joint structure of an air compressor cylinder head and a valve seat plate, which comprises a main bearing housing, a cylinder, a valve seat plate, a cylinder head, and a valve seat plate or/and
  • the cylinder head is fastened to the bolt on the main bearing seat, the cylinder is placed between the valve seat plate and the main bearing seat, the valve seat plate is placed between the cylinder head and the cylinder, and the cylinder is pressed against the main bearing seat by the valve seat plate
  • the utility model is characterized in that at least one main bearing seat, one cylinder, one valve seat plate and one cylinder head participate in the same pump head which constitutes the compressor, and the valve seat plate or/and the cylinder head are tightly arranged in the pump head.
  • the number of bolts fixed to the main bearing housing does not exceed three.
  • the compressor of the above-mentioned cylinder head and valve seat plate fastening structure has a total of two pump heads, and at least one of the two pump heads uses no more than two bolts to drive the respective pump heads.
  • the seat plate or/and the cylinder head are fastened to their main bearing seats, while the two pump heads share a single motor for driving and Separated at the ends of the motor.
  • the compressor for the above-mentioned cylinder head and valve seat plate fastening structure is a two-cylinder compressor, and the two pump heads are fastened to the valve seat plate or/and the cylinder head of the respective pump head by using no more than two bolts.
  • All of the above uses two or more bolts to fasten the seat plate or/and the cylinder head of the respective pump head to the two-cylinder compressor on the main bearing housing.
  • the working progress of the two pump heads is 180 in the running phase. degree.
  • the two pump heads are used to fasten the valve seat plate or/and the cylinder head to the main bearing housing, wherein at least one of the two bolts of the pump head is separated by the cylinder of the pump head and both The bolt axis of the bolt is parallel to the cylinder axis of the cylinder in the pump head and the three axes lie in a plane.
  • the pump head has at least one pump head, and the number of bolts for fastening the valve seat plate or/and the cylinder head to the main bearing seat thereof is two, and at least one of the two bolts directly acts on the same.
  • the cylinder head of the pump head and through the cylinder head press the valve seat plate and cylinder against the main bearing housing.
  • the pump head has at least one pump head, and the number of bolts for fastening the valve seat plate or/and the cylinder head to the main bearing seat thereof is two, and at least one of the two bolts directly acts on the same.
  • the cylinder plate on the pump head and through the valve seat plate presses the cylinder against the main bearing housing.
  • At least one pump head is disposed on the pump head, and at least one bolt on the pump head applies a force of the bolt to two different parts of the cylinder head of the pump head through a beam structure, the beam structure is on the cylinder head Directly open, or the beam structure is constructed by a separate beam member.
  • At least one pump head is disposed on the pump head, and a bolt is applied to the two different parts of the pump seat plate by a beam structure through a beam structure, the beam structure is Valve The seat plate is directly opened or the beam structure is constructed by a separate beam member.
  • At least one of the pump heads has only one bolt for fastening the valve seat plate or/and the cylinder head to the main bearing housing, and the side of the pump head opposite the cylinder from the bolt
  • a hook member is provided to hook the cylinder head with the main bearing housing, the hook member is a separate member or the hook member is integrally formed with the main bearing housing.
  • At least one of the pump heads has only one bolt for fastening the valve seat plate or/and the cylinder head to the main bearing housing, and the pump head is opposite to the bolt by the cylinder
  • the side is provided with a hook member for hooking the valve seat plate with the main bearing seat, the hook member is a separate member or the hook member is integrally formed with the main bearing seat, and the cylinder head and the valve in the pump head are The seat plates are joined together by fastening screws.
  • the pump head is fastened to the main bearing housing by two bolts, and at least one of the two bolts of the pump head is arranged side by side on the same side of the cylinder and is interposed.
  • the side of the cylinder opposite to the two bolts is provided with a hook member for hooking the cylinder head or the valve seat plate with the main bearing seat, the hook member is a separate member or the hook member is integrated with the main bearing seat Structure production.
  • the main bearing housing is provided with a convex or concave opening, and the main bearing seat is positioned and connected to the casing of the compressor motor through the convex or concave openings.
  • the above cylinder has a thin-walled cylindrical shape and has a double-flap structure at its both ends.
  • the present invention has the outstanding advantage over the prior art in that the cylinder head and the valve seat plate are fastened to the main bearing seat by using no more than three bolts, which is substantially larger than the conventional structure in which not less than four bolts are fastened.
  • the number of parts of the compressor is reduced, on the one hand, the processing and workload are reduced, on the other hand, the installation and commissioning are reduced, and the difference in the material of the parts is reduced, in particular, the installation and the position of the compressor
  • the main bearing housing of the crankshaft has also been greatly simplified, thereby effectively improving the fastening of the bolts.
  • the consistency of the degree can improve the working reliability of the compressor, reduce the manufacturing cost of the compressor, and reduce the material of the compressor.
  • FIG. 1 is a schematic view showing the axial connection and explosion assembly of an embodiment of an air compressor cylinder head and a valve seat plate fastening structure of an air compressor in which only one fastening bolt is arranged and pressed against a cylinder head;
  • FIG. 2 is a schematic view showing the axial connection and explosion assembly of an embodiment of an air compressor cylinder head and a valve seat plate fastening structure of a single pump head in which only one fastening bolt is arranged and pressed against a valve seat plate;
  • FIG. 3 is a schematic view showing the axial connection and explosion assembly of an embodiment of an air compressor cylinder head and a valve seat plate fastening structure of the air compressor of the present invention, in which only two fastening bolts are arranged and pressed against the cylinder head;
  • Figure 4 is a perspective view showing the axial connection and partial embodiment of the air cylinder head and the valve seat plate of the air compressor of the present invention shown in Figure 3, in which only a plurality of fastening bolts are arranged on the cylinder head and pressed against the cylinder head. Schematic cross-sectional view;
  • Figure 5 is a view showing the fastening structure of the air cylinder head and the valve seat plate of the air compressor of the present invention shown in Figure 3 arranged in a two-cylinder compressor, and each pump head is arranged only with two fastening bolts and pressed against the cylinder head Schematic view of an embodiment of the embodiment in which one of the pump heads removes the cylinder head, valve seat plate, cylinder and bolt;
  • FIG. 6 is a schematic view showing the axial connection and explosion assembly of an embodiment of an air compressor cylinder head and a valve seat plate fastening structure of the air compressor of the present invention in which only two fastening bolts are arranged and pressed against the valve seat plate;
  • FIG. 7 is a schematic view showing axial assembly and explosion assembly of an embodiment in which a fastening structure of an air compressor cylinder head and a valve seat plate is arranged with an integral beam structure to press a cylinder head;
  • FIG. 8 is a schematic view showing axial assembly and explosion assembly of an embodiment of a pneumatic compressor cylinder head and a valve seat plate fastening structure of the air compressor according to the embodiment of the present invention
  • Figure 9 is a view showing the overall arrangement of the fastening structure of the air cylinder head and the valve seat plate of the air compressor of the present invention Schematic diagram of axial and explosive assembly of an embodiment of a beam structure compacting valve seat plate;
  • FIG. 10 is a schematic view showing axial assembly and explosion assembly of an embodiment of a fastening structure of a cylinder head and a valve seat plate of an air compressor according to the present invention, in which a split beam structure is pressed;
  • FIG. 11 is a schematic view showing the axial connection and explosion assembly of an embodiment of an air compressor cylinder head and a valve seat plate fastening structure of the air compressor according to an embodiment in which a single pump head is arranged with three fastening bolts and all are tightened on the main bearing housing body;
  • Figure 12 is a plan view showing the fastening structure of the air cylinder head and the valve seat plate of the air compressor of the present invention.
  • the single pump head is arranged with three fastening bolts and all of them are tightened on the main bearing housing body. (One of the pump heads removes the cylinder. Schematic diagram of cover, valve seat plate, cylinder and bolt);
  • Figure 13 is a view showing the fastening structure of the air cylinder head and the valve seat plate of the air compressor of the present invention.
  • the single pump head is arranged with three fastening bolts and the two are fastened to the main bearing housing body and the other one is tightened on the motor casing.
  • a schematic view of an example one of which is removed from the cylinder head, valve seat plate, cylinder and bolt);
  • Figure 14 is a schematic view showing the axial connection and explosion assembly of an embodiment of an air compressor cylinder head and a valve seat plate fastening structure of a single air pump compressor with two fastening bolts arranged with a structural member;
  • Fig. 15 is a schematic exploded view showing an embodiment of an assembly structure of a main bearing housing and a motor of a fastening structure of an air compressor cylinder head and a valve seat plate according to the present invention.
  • a fastening structure of a cylinder head and a valve seat plate of an air compressor comprising a main bearing housing 1, a cylinder 2, a valve seat plate 3, a cylinder head 4, and fastening the valve seat plate 3 or/and the cylinder head 4 a bolt 5 to the main bearing housing 1, wherein the cylinder 2 is placed between the valve seat plate 3 and the main bearing housing 1, the valve seat plate 3 is placed between the cylinder head 4 and the cylinder 2, and the cylinder 2 is pressed by the valve seat plate 3.
  • the air compressor with the fastening structure of the cylinder head 3 and the valve seat plate 4 of the present invention is further provided with main bearing 6, crankshaft 7, connecting rod 8 and piston 9 and the like, wherein the crankshaft 7 is supported by the main bearing 6 in the main bearing
  • the seat 1 is rotated by the motor A, and the piston 9 is mounted in the cylinder 2 and driven by the crankshaft 7 through the connecting rod 8 to reciprocate relative to the cylinder 2;
  • the greatest feature of the present invention is that Among the components constituting the compressor main body, at least one main bearing housing 1, one cylinder 2, one valve seat plate 3, and one cylinder head 4 collectively participate in the same pump head B constituting the compressor, and in the pump head B
  • the number of bolts 5 that fasten their seat plate 3 or/and cylinder head 4 to their main bearing block 1 does not exceed three; it should be noted that the number of pump heads B of such a configuration is present in the same compressor.
  • the compressor is a single cylinder compressor. If there are two cylinders 2, Two-cylinder compressor, and so on if there are n cylinders 2, it is n-cylinder compression
  • a single-cylinder compressor with a pump head B and a two-cylinder compressor with two pump heads B having the present invention are more a good form of compressor, in particular, a two-cylinder compressor with a dual pump head B
  • the two pump heads B can be placed at the two axial ends of the motor A (as shown in Figures 1 to 4), or together Arranged at the same shaft end of the motor A (not shown);
  • the bolts 5 for fastening the valve seat plate 3 or/and the cylinder head 4 to the main bearing housing 1 can be arranged in three ways: 1) when the pump head B is a case where a bolt 5 is used to fast
  • the bolt 5 is located as far as possible should link the swinging plane 8, and the bolt of the bolt 5 and the cylinder axis Oa 2
  • the cylinder axis Ob should be set as parallel as possible; 2) when the pump head B is used to tighten the seat plate 3 and the cylinder head 4 by using two bolts 5 (as shown in Figs.
  • the number of bolts 5 is greatly reduced compared to the conventional mounting method, and the force condition of the bolts 5 can be improved by optimizing the layout of the two bolts 5, wherein a preferred layout is to place the two bolts 5 on both sides of the cylinder 2 And the bolt axis Oa of the two bolts 5 is parallel and coplanar with the cylinder axis Ob of the cylinder 2 (as shown in FIG. 5), whereby the bolt axis Oa and the cylinder 2 of the two bolts 5 can be reduced or even completely eliminated.
  • the additional torque acting on the bolt 5 derived from the cylinder axis Ob not coplanar (assuming that the resultant force of the gas acting on the valve seat plate 3 when the gas is compressed is along the direction of the cylinder axis Ob, the cylinder axis Ob to the plane of the two bolt axis Oa
  • the additional torque is equivalent to the product of the combined force of the gas compression and the offset distance, which is the same as below, thereby improving the operational reliability of the bolt 5; in addition, when only two bolts 5 are used to tighten the valve When the seat plate 3 or the cylinder head 4 is used, it should be as far as possible
  • the two bolts 5 are arranged in the rocking plane of the connecting rod 8, so that the structure of the main bearing housing 1 can be simplified, since the axial direction of the motor A (also the axial direction of the crankshaft 7) is observed at this time, the two bolts 5
  • the layout of the main bearing block 1 can be made shorter, or the main bearing block 1 can be made shorter (of course, the axial length
  • the two bolts 5 can be arranged side by side and tightened on the main bearing housing 1 (as shown in FIG. 14). It is even possible to tighten one bolt 5 to the main bearing housing 1 and the other bolt 5 to the casing of the motor A (not shown); 3) when the pump head B is three bolts 5 To tighten the seat plate 3 and the cylinder head 4 (as shown in Figures 11 to 13), the bolt 5 can achieve a more flexible layout, such as tightening all three bolts 5 to the main bearing.
  • the body of the seat 1 (one of which is arranged next to one side of the cylinder 2 and the other two are arranged side by side on the other side of the cylinder 2, Double bolts 5 with a single column layout bolts 5 are separated by the cylinder 2, as shown in FIG. 11 and FIG. 12),
  • the three bolts 5 have two bolts which are fastened to the main bearing housing 1 to form a main bolt, and the remaining one bolt 5 can be tightened on the casing of the motor A to become an auxiliary bolt (see Fig. 13).
  • the main bolt (bearing the main force) should be as close as possible or fall in the rocking plane of the compressor connecting rod 8, and the auxiliary bolt (preventing the amplitude or deformation of the valve seat plate 3 and some parts of the cylinder head 4 from being excessive) can be It is necessary to implement a flexible arrangement; in particular, the operation of the compressor in the present invention is driven by the motor A. Since the main bearing housing 1 and the housing of the motor A are fastened, all bolts are used.
  • the bolt 5 in the case of fastening to the casing of the motor A, whether it is directly fastened to the casing of the motor A or indirectly fastened to the casing of the motor A by other members, it is regarded as the bolt 5 in the present invention
  • the main bearing housing 1 is fastened, that is, to the extent that the valve seat plate 3 or/and the cylinder head 4 is fastened to the main bearing housing 1 by bolts 5, and it can be considered that the housing of the motor A is the main bearing housing 1 Extension or it is part of the main housing 1; additional
  • the rocking plane of the connecting rod 8 in the present invention refers to a plane in which the connecting rod 8 performs a planar movement during operation, the plane passing through the cylinder axis Ob of the cylinder 2 and perpendicular to the axis of rotation of the crankshaft 7.
  • the actual rocking plane of the connecting rod 8 is not a completely ideal stationary plane, considering the existence of various mating gaps and various errors due to manufacturing, assembly, force deformation and temperature deformation, and thus the present invention
  • the rocking plane of the connecting rod 8 mentioned therein should include a certain dynamic surface characteristic, which allows rocking, or turbulence, or fluctuation within a certain range of amplitude, which is said to coincide with the rocking plane of the connecting rod 8 in the future.
  • the context means that as long as it coincides with a certain dynamic rocking plane of the connecting rod 8 at a certain moment, it can be considered that the two satisfy the condition of coincidence, and similarly, the context of parallel with the rocking plane of the connecting rod 8 in the future is also It means that as long as it is parallel with a certain dynamic rocking plane of the connecting rod 8 at a certain moment, it can be considered that the two meet the parallel condition; it should also be noted that the present invention relates to the use of the bolt 5 to the valve seat plate 3 or/and
  • the content of the cylinder head 4 fastened to its main bearing housing 1 or a discussion and description similar to this content refers to one of the following three aspects of behavior or content: 1) in the same pump head All of the bolts 5 on B are directly pressed against the cylinder head 4 and the valve seat plate 3 and the cylinder 2 which are echoed by the cylinder head 4 are pressed or pressed against the main bearing housing 1 (Fig.
  • the number of parts of the compressor can be reduced and thus the machining and installation work can be reduced, and on the other hand, the structure of the main bearing block 1 can be simplified by reducing the installation position; firstly, the compressor can be lowered accordingly. Manufacturing costs and reduction of compressor manufacturing materials are unquestionable; secondly, the reduction of production links and the large number of parts have reduced the probability of errors during manufacturing, installation and commissioning, and even the core components such as bolts.
  • the degree of material difference between 5 can also be reduced; in other words, the fastening structure of the cylinder head 4 and the valve seat plate 3 of the air compressor based on the above positive effects is not only advantageous but also fully achievable in the present invention.
  • the utility model can effectively improve the consistency of the fastening degree of each bolt 5 and effectively improve the working reliability of the compressor.
  • the number of pump heads B of the compressor may be set to two, and at least one of the two pump heads B is a valve seat of the respective pump head B using no more than two bolts 5
  • the plate 3 or / and the cylinder head 4 are fastened to the main bearing housing 1, while the two pump heads B share a motor A for driving and are disposed at both ends of the motor A, that is, both
  • the pump heads B are arranged at the two shaft ends of the motor A (as shown in FIGS. 1 to 14).
  • each pump head B is correspondingly provided with a main bearing housing 1 and is disposed at one end of the motor A.
  • the compressor is a two-cylinder compressor at this time, that is, the compressor has only two cylinders 2, two pistons 9, two connecting rods 8, two Main bearing 6 (each pump head B is generally only equipped with one main bearing 6 and built in its main bearing housing 1 if the pump head B needs to be equipped with two main bearings 6 and is built in close proximity to its main bearing housing 1
  • the invention will regard the two main bearings 6 which are arranged next to each other as an equivalent main bearing 6, that is, the category in which the pump head B is only provided with one main bearing 6, and a crankshaft 7 (the curved piece 7) Both ends of the head 7 are each provided with a connecting rod for driving the crank pin 8).
  • the two-cylinder compressor with double pump head B and divided at the two ends of the motor A is the two-headed layout compressor which is now commonly known as the two-head layout compressor.
  • the compressor of this type can maximize the utilization of the motor A.
  • Working characteristics, and better layout design; in particular, the best two-headed layout compressor is that the two-cylinder compressor has two and only two pump heads B with no more than two bolts 5 Fastening the valve seat plate 3 or/and the cylinder head 4 of the respective pump head B to the main bearing housing 1 of its pump head B, and operating the two pump heads B of the two-cylinder compressor on the operating phase Arrange for a difference of no less than 45 degrees (or a difference of not less than In this case, it means that when the piston 9 in one of the pump heads B is operated to the top dead center, the piston 9 in the second pump head B must reach the top dead center after the crankshaft 7 is again operated to an angle of 45 degrees or more.
  • the advantage of this method is that the maximum compression force of the two pump heads B can be separated by a phase without overlapping as much as possible, which is very advantageous for the reliability of the compressor and the noise reduction, especially when the two
  • the working process of the pump head B is arranged 180 degrees out of phase (or the phase difference is ⁇ radians)
  • the two bolts 5 of at least one of the pump heads B can be arranged. Beside the two sides of the cylinder 2 to which the pump head B belongs, in other words the two bolts 5 are separated by the cylinder 2 of the pump head B, and the bolt axis Oa of the two bolts 5 and the cylinder 2 in the pump head B.
  • the cylinder axis Ob is parallel and the three axes lie in a plane. This is the case in Figure 5.
  • the parallelism of the axis in the present invention is a containment concept, which allows a slight non-parallel between the respective axes due to manufacturing errors, assembly errors, force deformation errors, and temperature deformation errors, as long as the axes are Parallel error values are limited to within the range of conventional mechanical engineering errors, ie they are considered to be parallel, for example, within the height dimension of cylinder 2 (ie, measured along the cylinder axis Ob), if the parallel error value of each axis does not exceed cylinder 2 Five percent of the diameter is considered to be parallel to each other; likewise, the fact that the three axes of the present invention are co-located in one plane is also an inclusive concept, which allows manufacturing errors, assembly errors, force deformation errors, and The theory of temperature deformation causes the theory to be non-coplanar.
  • the bolt 5 can press the valve seat plate 3 against the cylinder 2 by the pre-tightening force, and at the same time can press the cylinder 2 against the main bearing housing 1, when the compressor is subjected to the compression stroke After the gas is compressed, it will inevitably generate resistance. It is known from the mechanics that the combined force of the resistance will act on the valve seat plate 3 along the cylinder axis Ob of the cylinder 2, and will eventually be transmitted to the bolt 5, requiring attention.
  • the piston 9 is also subjected to the compressive force of the gas and is finally transmitted to the bolt 5 (the transmission path is: piston 9 ⁇ connecting rod 8 ⁇ crankshaft 7 ⁇ main bearing 6 ⁇ main bearing housing 1 ⁇ bolt 5), It can be seen that the resultant force of the compressed gas-derived reactive force must be transmitted to the bolt 5, at which time the bolt 5 will withstand a strong force but still need to maintain sufficient fastening force to maintain the cylinder head 4, the valve seat plate 3, the cylinder 2 No looseness occurs between the main bearing housings 1.
  • the bolt 5 is only purely Axial force without additional torque At this time, the force condition of the bolt 5 does not deteriorate, so that the operational reliability of the bolt 5 can be improved.
  • the bolt axis Oa is parallel and coplanar with the cylinder axis Ob, so that this plane can coincide with the rocking plane of the connecting rod 8, so that not only the stress state of the bolt 5 but also the structure of the main bearing housing 1 can be simplified.
  • the valve seat plate 3 or/and the cylinder head 4 are fastened to its main bearing block 1
  • the number of the bolts 5 is set to two in total, and at least one of the two bolts 5 directly acts on the cylinder head 4 of the pump head B, and the valve seat plate 3 and the cylinder 2 are pressed by the cylinder head 4.
  • the sealing between the valve seat plate 3 and the cylinder head 4 can be realized without any other measures.
  • the cylinder head 4 and the valve seat plate 3 can also be used using the fastening screw 10. When tightened together, the sealing performance of the two will be more reliable.
  • At least one of the pump heads B, a bolt 5 for fastening its seat plate 3 or/and cylinder head 4 to its main bearing block 1 The number of the two bolts is two in total, and at least one of the two bolts 5 directly acts on the valve seat plate 3 of the pump head B, and the cylinder 2 is pressed against the main bearing housing 1 through the valve seat plate 3.
  • a preferred practice at this time is to fasten the valve seat plate 3 and the cylinder head 4 together using at least one fastening screw 10.
  • the beam structure 11 can be directly opened on the cylinder head 4 (the beam structure 11 at this time is an integral beam, as shown in FIG. 7), and the beam structure 11 can also be formed by an independent beam member 11a. (At this time, the beam structure 11 is a split beam, as shown in FIG. 8), the direct opening on the cylinder head 4 can be realized by the hollow structure 43; it should be noted that the force of the bolt 5 is respectively applied to the cylinder.
  • the two different parts of the cover 4 have the advantage of making the distribution of the force wider and more reasonable, which can improve the stress distribution of the force receiving parts such as the cylinder head 4 and the valve seat plate 3, and can improve the cylinder head 4 Sealing property with the seat plate 3.
  • the two different parts of the beam 3 can be opened directly on the valve seat plate 3 (of course, the beam structure 11 is an integral beam, as shown in FIG.
  • the beam member 11a is constructed (of course, the beam structure 11 at this time is a split beam, as shown in Fig. 10), and it can be realized directly on the valve seat plate 3 or by the hollow structure 43.
  • the pump head B there may be at least one pump head B which has only one bolt number 5 for fastening the valve seat plate 3 or/and the cylinder head 4 to the main bearing housing 1, in which the pump head B is Separated from the bolt 5
  • the opposite side of the cylinder 2 is provided with a hook member 12 for hooking the cylinder head 4 with the main bearing housing 1, the hook member 12 may be a separate member (as shown in FIG.
  • the main bearing housing 1 is made of a unitary structure (not shown), and the number of the hook members 12 may be one or two or more; it should be noted that the purpose of providing the forming member 12 is It is possible to reduce the number of the bolts 5, and on the other hand, it is possible to improve the mounting efficiency, that is, the task of fastening the valve seat plate 3 or/and the cylinder head 4 can be completed by simply tightening a smaller number of bolts 5. Similarly, in the present invention, there may be at least one pump head B which has only one bolt number 5 for fastening the valve seat plate 3 or/and the cylinder head 4 to the main bearing housing 1 in the pump.
  • a hook member 12 is hooked between the head B and the side of the bolt 5 opposite to the cylinder 2, and the valve seat plate 3 is hooked together with the main bearing housing 1.
  • the hook member 12 can be a separate member (as shown in FIG. 2).
  • the hook member 12 is integrally formed with the main bearing housing 1 (not shown), and the cylinder head 4 and the valve seat plate 1 of the pump head B can be connected together by a fastening screw 10.
  • the pump head B which fastens the valve seat plate 3 or/and the cylinder head 4 to the main bearing housing 1 by means of two bolts 5 allows two of the at least one pump head B
  • the root bolts 5 are juxtaposed on the same side of the cylinder 2, and a hook member 12 is provided on the side opposite to the two bolts 5 via the cylinder 2, and the cylinder head 4 or the valve seat plate 3 is hooked to the main bearing housing 1
  • the hook member 12 can be a separate piece (as shown in FIG. 14) or the hook member 12 can be made in one piece with the main bearing housing 1 (not shown).
  • a male opening 1a may be provided on the main bearing housing 1, through which the main bearing housing 1 passes.
  • the port 1a is positioned and connected to the casing of the motor A of the compressor.
  • the casing of the motor A can be slightly extended with respect to the stator of the motor A to become a concave sunken platform A1, the main body of the concave sunken platform A1.
  • the inner wall of the casing of the motor A see FIGS.
  • the concave platform A1 abuts the convex opening 1a of the main bearing housing 1 to form a positioning fit; in addition, a concave stop is provided on the main bearing housing 1 a structure (not shown), and the concave end is positioned and connected to the outer circumference of the motor A casing (corresponding to the outer edge boss), that is, the outer edge of the casing of the motor A is positioned and embedded in the main bearing Inside the concave stop on the seat 1; it should be noted that for the two-cylinder compressor with two-headed layout, the main bearing housing 1 can be provided with a convex stop 1a at both ends of the motor A at the same time.
  • the matching structure of the concave block A1 of the motor A can also be used at the both ends of the motor A.
  • the main bearing housing 1 is provided with a concave ring to match the outer peripheral edge of the motor A casing (in the figure) Not shown), it is also possible to adopt a structure in which the main bearing housing 1 is provided with a convex seat 1a and a motor A barrel concave sunken table A1 at the both ends of the motor A, and the main bearing seat 1 is used at the other end.
  • a configuration (not shown) in which the concave end is matched with the outer circumference of the casing of the motor A is provided.
  • the cylinder 2 in order to save material and mount reliability, can be configured as a thin-walled shell-like structure, and the cylinder 2 has the structure of two flanges 2a, that is, double-flanges 2a (see FIG. 4 and FIG. 7 to FIG.
  • the cylinder 2 has a structure with a flange 2a at both axial ends thereof; the cylinder 2 adopts a thin-walled shell structure to facilitate heat dissipation, which is advantageous for improving the working reliability of the compressor, and at the same time
  • the thin-walled shell can be made of profile or obtained by deep drawing of the sheet, which is beneficial to mass production and reduces the production cost; compared with the conventional cylinder 2 with only a single flange 2a (see Figures 1 to 3, Figure 6, Figure 11 and Figure 14), the structure of the cylinder 2 with double flange 2a brings at least three advantages: the first advantage is that the worker does not need to select the cylinder 2 during installation (traditional thin with a single flange 2a)
  • the wall-cylinder-shaped cylinder 2 has its sole flange 2a disposed toward one side of the valve seat plate 3 and is in close contact with the sealing strip of the valve seat plate 3 to prevent high-pressure gas leakage, and the flange 2a must be recognized during assembly.
  • the orientation cannot be reversed, but in the actual production process, the workers It is often the case that the misplaced orientation causes the compressor to malfunction, that is, the reliability of the compressor is reduced.
  • the practice of selecting the edge is obviously improved, and the cost is saved, and the misassembly is also reduced.
  • the advantage is that for the main bearing block 1 or the valve seat plate 3, The contact area between the cylinders 2 and their cylinders is relatively large. Compared with the structure of the conventional single flange 2a, the structure of the double flanges 2a is not only more securely installed, but also the value of the contact specific pressure between them is smaller, so that it can be improved.
  • the reliability of these mountings can also improve the operational reliability of the compressor; the third advantage is that the cylinder 2 can be enhanced to resist deformation. Due to the thin shell structure, the cylinder 2 itself has less rigidity and its compression resistance. (The bolt 5 preload force is caused by) and the tensile strength (caused by the gas compression force) are relatively weak, and it is obvious that adding a structure of the flange 2a can significantly increase the bending modulus of the cylinder 2, in other words, the present invention.
  • the double flange 2a structure of the cylinder 2 will have a better rigidity than the conventional single flange 2a structure of the same thin shell structure, that is, the cylinder 2 of the double flange 2a structure of the present invention has better operational reliability.
  • the present invention has the outstanding advantage over the prior art that the same pump head B uses no more than three bolts 5 to fasten the cylinder head 4 and the valve seat plate 3 to the main bearing housing 1, with a tradition of not less than four Compared with the structure in which the root bolt 5 is fastened, the number of parts of the compressor is greatly reduced, on the one hand, the processing procedure and the workload are reduced, on the other hand, the installation and debugging are also reduced, and the materials of the same batch are reduced.
  • the tendency of the difference, in particular, the main bearing housing 1 of the crankshaft 7 of the compressor and the in-position compressor is also greatly simplified, thereby effectively improving the consistency of the fastening degree of each bolt 5, and at the same time improving the compressor Work reliability, reduce compressor manufacturing costs, and reduce compressor manufacturing materials.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

L'invention concerne une structure de raccordement sûre destinée à une culasse et une plaque de siège de soupape d'un compresseur d'air, comprenant un siège (1) de palier principal, un cylindre (2), une plaque (3) de siège de soupape, une culasse (4) et un boulon (5) de fixation destiné à raccorder de manière sûre la plaque (3) de siège de soupape et/ou la culasse (4) au siège (1) de palier principal. Le cylindre (2) est disposé entre la plaque (3) de siège de soupape et le siège (1) de palier principal ; la plaque (3) de siège de soupape est placée entre la culasse (4) et le cylindre (2) ; le cylindre (2) est pressé contre le siège (1) de palier principal par la plaque (3) de siège de soupape ; le nombre des boulons (5) destinés à solidariser la plaque (3) de siège de soupape et/ou la culasse (4) au siège (1) de palier principal est inférieur ou égal à trois. Le nombre de boulons est réduit. Par conséquent, d'un côté, le nombre de pièces d'un compresseur peut être réduit, et les charges de travail d'usinage et l'installation sont réduites ; d'autre part, la structure du siège de palier principal peut être simplifiée, de sorte que le maintien de l'étanchéité de tous les boulons est amélioré, la fiabilité de fonctionnement du compresseur est améliorée, et les coûts de fabrication du compresseur sont réduits.
PCT/CN2015/097273 2015-11-21 2015-12-14 Structure de raccordement sûre pour culasse et plaque de siège de soupape de compresseur d'air WO2017084133A1 (fr)

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CN201510812895.3 2015-11-21
CN201510812895.3A CN105298807B (zh) 2015-11-21 2015-11-21 一种空气压缩机气缸盖及阀座板的紧固连接结构

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CN106762550A (zh) * 2017-03-03 2017-05-31 浙江鸿友压缩机制造有限公司 一种轻量化泵头座架及配有该泵头座架的无油空气压缩机
CN110173418A (zh) * 2019-01-10 2019-08-27 苏州欧圣电气股份有限公司 一种空气压缩泵及空压机
CN109773362B (zh) * 2019-03-28 2023-09-26 昆山华恒焊接股份有限公司 压缩机焊接系统

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JPS63183287A (ja) * 1987-01-23 1988-07-28 Matsushita Refrig Co 往復動型圧縮機
JPS63230975A (ja) * 1987-03-19 1988-09-27 Sanyo Electric Co Ltd 密閉型圧縮機
US6227821B1 (en) * 1996-06-28 2001-05-08 Thomas Industries Inc. Two-cylinder pump
CN102852768A (zh) * 2005-05-17 2013-01-02 托马斯工业公司 改进的泵

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CN202468207U (zh) * 2012-03-09 2012-10-03 张立武 一种陶瓷缸无油空气压缩机
CN102748270A (zh) * 2012-05-30 2012-10-24 李官镐 具有防尘结构的皮带传动无油波型空气压缩机
CN203297068U (zh) * 2013-06-08 2013-11-20 宁波华生压缩机有限公司 低噪稳定型无油压缩机
CN203297059U (zh) * 2013-06-08 2013-11-20 宁波华生压缩机有限公司 静音无油型空压机
CN205349669U (zh) * 2015-11-21 2016-06-29 浙江鸿友压缩机制造有限公司 一种空气压缩机气缸盖及阀座板的紧固连接结构

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63183287A (ja) * 1987-01-23 1988-07-28 Matsushita Refrig Co 往復動型圧縮機
JPS63230975A (ja) * 1987-03-19 1988-09-27 Sanyo Electric Co Ltd 密閉型圧縮機
US6227821B1 (en) * 1996-06-28 2001-05-08 Thomas Industries Inc. Two-cylinder pump
CN102852768A (zh) * 2005-05-17 2013-01-02 托马斯工业公司 改进的泵

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CN105298807A (zh) 2016-02-03

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