WO2017133158A1 - 直联式空气压缩机电机紧固连接结构 - Google Patents

直联式空气压缩机电机紧固连接结构 Download PDF

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Publication number
WO2017133158A1
WO2017133158A1 PCT/CN2016/085957 CN2016085957W WO2017133158A1 WO 2017133158 A1 WO2017133158 A1 WO 2017133158A1 CN 2016085957 W CN2016085957 W CN 2016085957W WO 2017133158 A1 WO2017133158 A1 WO 2017133158A1
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WO
WIPO (PCT)
Prior art keywords
hole
motor casing
motor
handle
pump head
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PCT/CN2016/085957
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English (en)
French (fr)
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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Application filed by 浙江鸿友压缩机制造有限公司 filed Critical 浙江鸿友压缩机制造有限公司
Publication of WO2017133158A1 publication Critical patent/WO2017133158A1/zh

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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
    • F04B39/14—Provisions for readily assembling or disassembling
    • 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

Definitions

  • the invention belongs to the technical field of compressors, and relates to a fastening connection structure of an air compressor motor, in particular to a direct-coupled air compressor that directly drives a compressor pump head by a motor, and a motor and a pump head body thereof A structure that is fastened to each other.
  • the direct-coupled air compressor is a large-scale electromechanical product widely used in decoration, health care, electronic packaging and food packaging industries.
  • the direct-coupled air compressor is an air compressor whose motor directly connects and drives the pump head. Because of the direct drive method, the speed of the direct-coupled compressor is relatively high; therefore, the compressor of this type
  • the overall machine volume can be made lighter and smaller than those of non-direct-coupled compressors (such as belt-driven air compressors).
  • the direct-coupled air compressor includes two components of a motor and a pump head, wherein the pump head includes components such as a cylinder, a piston, a connecting rod, a crankshaft and a main bearing seat, and the rotor of the motor directly drives the crankshaft and the piston connecting rod assembly to operate, or The rotor shaft of the motor is simply the body of the pump head crankshaft and directly drives the piston rod assembly to operate. It is well known that where the motor of a direct-coupled air compressor must be fastened to the pump head of the compressor, the existing fastening method uses several (usually four) long bolts that extend beyond the length of the compressor stator.
  • these bolts are arranged close to the stator of the motor and axially penetrate or span the stator, so as to pull the stator of the motor or the outer casing of the motor from the axial direction. Relying on the main bearing housing, the purpose of fastening the motor is achieved.
  • the diameter ratio is usually more than twenty to one, which is a typical ultra-long thin rod structure, so much so that The torsional stiffness of the bolt is difficult to withstand greater tightening torque, so the tightening force of the fastening bolt is often small; it is well known that the speed of the direct-coupled air compressor is very high, and its vibration frequency is much higher than other types of reciprocating
  • the compressor in addition to the direct-coupled compressor motor, is often supported by a cantilever structure with one end free from the other end (at least for the single-cylinder air compressor with the largest output), and the small tightening torque is very small. It is easy to cause the bolt fastening to fail and eventually the motor is loose.
  • the long bolt fastening motor is structurally poor in fastening quality.
  • the use of long bolts in the form of fastening members increases the production cost of the compressor.
  • the longer length will inevitably increase the material cost of the bolts.
  • the longer bolts will inevitably increase the manufacturing cost: on the one hand, the long bolts are not easy to install.
  • Quasi-mounting holes especially when the motor is provided with an outer casing and is positioned by the outer casing and the main bearing housing of the pump head, the long bolts are often traversed from the casing of the motor and are mated with the threaded holes of the main bearing housing of the pump head
  • the fastening action at this time is a blind vision operation mode, and the difficulty of seating is not difficult to imagine, thereby causing a decrease in production efficiency and thereby increasing labor costs; on the other hand, since the long bolts inevitably increase the weight and volume, Deriving more handling and storage costs, not only in the production process, but also in the process of packing freight, especially in export freight, although the above cost increase is negligible for a single compressor product, However, it is noted that direct-coupled air compressors are usually produced in large quantities, and the effect of sand-forming towers will highlight considerable additional costs.
  • the present invention provides a motor-fastening connection structure for a direct-coupled air compressor, which aims to improve compression by improving and updating a conventional fastening structure.
  • the quality of the connection between the machine motor and the pump head, and effectively reduce the production cost of the compressor is a motor-fastening connection structure for a direct-coupled air compressor, which aims to improve compression by improving and updating a conventional fastening structure.
  • the object of the present invention is achieved by: a direct-connected air compressor motor fastening connection structure, package
  • the motor casing, the pump head main bearing seat and the fastening bolt are characterized in that: a slot-shaped hole is formed in the motor casing, and the slot-shaped hole is located at an end of the motor casing near the main bearing seat of the pump head, and is additionally provided There is a handle clip corresponding to the slot-shaped hole, wherein a mutual bearing relationship exists between the handle clips and the slot-shaped holes which are mutually assembled, and the structure in which the motor sleeve and the pump head main bearing seat are fastened to each other includes There are one of the following three situations: a) a first threaded hole is provided on the handle card, and a second through hole corresponding to the pump head main bearing seat is provided, and the fastening bolt passes through the second through hole.
  • the hole is screwed with the first threaded hole to tighten the motor casing and the pump head main bearing seat; b) the first through hole is provided on the handle card, and the pump head main bearing seat is provided with Reciprocating a second threaded hole, the fastening bolt passes through the first through hole and is screwed with the second threaded hole to tighten the motor casing and the pump head main bearing seat; c) is disposed on the handle card There is a first through hole and a pump head main bearing at the same time It is provided with a second through-hole matched by the fastening bolt through the second through-hole and the first through-hole and a nut screwed to the motor housing and the cylinder head main bearing mutually tensioned.
  • the above-mentioned pump head main bearing housing is provided with a stop structure and a motor cylinder shell for positioning.
  • the handle card member is a separate member, and the handle card member has one end abutting on the inner edge of the slot-shaped hole, and the other end of the handle card member is abutted on the pump head main bearing seat, and the handle card member is disposed on the handle card member.
  • the first threaded hole or the first through hole is disposed in a central portion of the handle clip.
  • the handle clip is provided with a positioning flange, the positioning flange is in contact with the wall surface of the motor casing and is limited by the motor casing, or the positioning flange is in contact with the main bearing seat of the pump head and is received by the pump head main bearing. The limit of the seat.
  • the handle card member is a separate piece and includes an "L" type structure.
  • One side of the handle card member and the wall surface of the motor tube case have abutting portion to become a fastening edge, and the other side of the handle card member passes through the motor casing.
  • the slotted hole becomes a radial pull, and the first threaded hole or the first through hole provided in the handle clip is laid out in the diameter Pull to the side.
  • the fastening edge of the handle clip is provided with a concave and concave structure, and the abutting portion of the fastening edge and the wall surface of the motor casing is separated from the radial tension by a certain distance.
  • the handle card member is a separate piece and includes a "U"-shaped structure.
  • the middle portion of the handle card member is a contact edge, and the two ends of the handle card member are bent toward the same lateral direction with respect to the contact side and respectively constitute a radial pull.
  • the edge and the limit constraint edge, the radial edge and the limit constraint edge respectively pass through the slotted hole in the motor casing, and the first threaded hole or the first through hole provided in the handle card is arranged in the radial edge or / and limit constraints on the edge.
  • a positioning boss structure is disposed on the radial pull edge or/and the limit constraint edge of the handle clip.
  • the radial pull edge and the limit constraining edge of the handle clip respectively pass through two mutually independent slot-shaped holes on the motor casing.
  • the handle card member is a separate member, and the handle card member is provided with a hook-shaped structure hooked on the inner edge of the slotted hole of the motor casing.
  • the handle clip is a separate piece and is snapped into the slotted hole of the motor casing, or the handle clip and the motor casing are made of one piece and punched into a curved arch shape by punching the slot hole of the motor casing .
  • the handle card member and the motor casing are an integral member, and the handle member is formed by bending and bending the residual material formed by the slotted hole of the punched motor casing.
  • the handle clip has a reinforced flange structure.
  • the first through hole formed in the handle card member is in the form of an open groove.
  • the second through hole formed in the main bearing housing of the pump head is in the form of an open groove.
  • the invention has the outstanding advantages that the length of the fastening bolt is greatly shortened by fastening the handle of the motor casing near the main bearing housing of the pump head, and the fastening bolt is greatly enhanced on the one hand.
  • Torsion stiffness which can withstand greater tightening forces, thereby effectively increasing the compressor
  • the quality of the connection between the motor and the pump head on the other hand, the short bolt connection not only saves the material of the bolts used, but also reduces the assembly difficulty of the bolts, thereby effectively reducing the production cost of the compressor.
  • FIG. 1 is a schematic exploded view of an embodiment of a direct-connected air compressor motor fastening connection structure including an embodiment of a contact force type handle card at both ends;
  • Figure 2 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 1;
  • FIG. 3 is a schematic exploded view showing the assembly of the direct-connected air compressor motor fastening connection structure of the direct-coupled air compressor of the present invention including the positioning flange holders;
  • Figure 4 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 3;
  • FIG. 5 is a schematic exploded view showing another embodiment of the direct-connected air compressor motor fastening structure of the present invention including a two-contact contact bearing handle member with a positioning flange;
  • Figure 6 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 5;
  • Figure 7 is a schematic exploded view showing the assembly of the "L" type handle card assembly of the direct-coupled air compressor motor fastening structure of the present invention
  • Figure 8 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 7;
  • FIG. 9 is a schematic exploded view showing an assembly of an embodiment of the "L" type handle fastener with a concave and concave structure of the direct-connected air compressor motor fastening connection structure of the present invention
  • Figure 10 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 9;
  • FIG. 11 is a schematic exploded view showing an embodiment of the direct-connected air compressor motor fastening structure of the present invention including a "U"-type handle card and each handle card member only matching one slot-shaped hole;
  • Figure 12 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 11;
  • Figure 13 is a view showing a fastening structure of a direct-connected air compressor motor of the present invention comprising a "U" type handle card And the assembly explosion diagram of each of the handle clips matching the two slotted holes embodiment;
  • Figure 14 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 13;
  • 15 is a schematic exploded view showing an assembly of a direct-connected air compressor motor fastening connection structure including a "U"-shaped handle card member and provided with a positioning boss structure;
  • Figure 16 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 15;
  • 17 is a schematic exploded view showing an assembly of a fastening type connection structure of a direct-coupled air compressor of the present invention including a hook-type handle card;
  • Figure 18 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 17;
  • 19 is a schematic exploded view showing the assembly of the snap-fit type handle member of the direct-coupled air compressor motor of the present invention including the snap-on type handle member integrally formed with the motor casing;
  • Figure 20 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 19;
  • 21 is a schematic exploded view showing the assembly of the fastener connection structure of the direct-coupled air compressor of the present invention including the handle member integrally formed with the motor casing;
  • Figure 22 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 21;
  • FIG. 23 is a schematic exploded view showing the assembly of the handle fastening structure of the direct-coupled air compressor motor of the present invention including a handle member integrally formed with the motor casing and configured with a nut;
  • Figure 24 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment shown in Figure 23;
  • 25 is a schematic exploded view of an embodiment of a handle of a direct-coupled air compressor motor fastening connection structure including an open slot-shaped through-hole according to the present invention
  • Figure 26 is a schematic cross-sectional view showing the assembled shaft and partial assembly of the embodiment of Figure 25.
  • the direct-connected air compressor motor fastening connection structure comprises a motor casing 1, a pump head main bearing housing 2 and a fastening bolt 3, wherein the motor stator 1c is disposed inside the motor casing 1 and fastened with the motor
  • the rotor 1b (including its rotating shaft) is supported on the bearing of the pump head main bearing housing 2, the motor rotor 1b is fastened with a crankshaft or the motor rotor 1b is integrally formed with the crankshaft, and the connecting rod of the compressor is directly driven by the motor rotor 1b.
  • the fastening bolt 3 used in the present invention is different from the case where the fastening bolt 3 used in the conventional compressor motor connection structure is a long bolt structure (in which case the length of the fastening bolt 3 exceeds the length of the motor stator 1c), the fastening bolt 3 used in the present invention
  • the length is a short bolt which is much shorter than the length of the motor stator 1c.
  • the present invention forms a slot-shaped hole 4 in the motor casing 1, which is located in the motor casing 1 near the pump head main bearing housing.
  • One end of the two ends (or one end of the two ends of the motor casing 1) is fastened to the pump main bearing housing 2, and the slotted hole 4 in the present invention is opened to be fastened to the main bearing housing 2 of the pump head.
  • a handle clip 5 corresponding to the slot-shaped hole 4 is provided, wherein the handle clips 5 and the slot-shaped holes 4 which are mutually assembled (ie, a pair having a mutual cooperation relationship) are mutually bearing.
  • the relationship between the motor casing 1 and the slotted hole 4 is when the motor casing 1 is fastened to the pump main bearing housing 2, or It is said that the handle card member 5 and the slot-shaped hole 4 are in contact with each other or connected to each other to receive and transmit the force of the fastening bolt 3; the structure of the motor casing 1 and the pump head main bearing housing 2 of the present invention is tightly connected to each other
  • the first punching through is provided on the handle card member 5.
  • the hole 5b is simultaneously provided with a second threaded hole corresponding to the pump head main bearing housing 2, and the fastening bolt 3 passes through the first through hole 5b and is screwed with the corresponding second threaded hole.
  • the motor casing 1 and the pump head main bearing housing 2 are tensioned with each other (not shown); c) the first through hole 5b is provided on the handle card 5, and the pump head main bearing housing 2 is disposed at the same time.
  • the fastening bolt 3 passes through the second through hole 2a and the first through hole 5b and is screwed with the nut 6 to connect the motor casing 1 and the pump head main bearing
  • the seats 2 are tensioned with each other (as shown in Figures 23 to 26).
  • the present invention includes the following two cases: in the first case, the nut 6 is laid on the side of the motor casing 1, and the fastening bolt 3 will be Firstly, the second through hole 2a is passed through the first through hole 5b and then screwed to the nut 6 (as shown in FIG. 23 to FIG.
  • the second case is that the nut 6 is arranged in the pump head main bearing seat 2 On this side, at this time, the fastening bolt 3 will first pass through the first through hole 5b and then through the second through hole 2a and then be screwed to the nut 6 (not shown); otherwise the nut 6 can be Conventional standard parts can also be specially made non-standard parts, either directly with the handle card 5 or with the pump head main bearing 2 or indirectly by other spacers.
  • the structure in which the motor casing 1 and the pump head main bearing housing 2 are fastened to each other in the present invention includes not only the use of one of the above three fastening structures, but also includes Using two or three of the above three fastening structures (ie, using various combinations thereof), and including at least one of the above three fastening structures and other fastening structures, in other words, as long as they exist
  • the fastening bolt 3 involved in the present invention can be disposed in the motor casing 1 or outside the motor casing 1 , that is, the fastening bolt 3 can be replaced by the motor casing 1 .
  • the fastening bolt 3 can also be arranged outside the outer cylindrical surface of the motor casing 1 to form an exposed bolt layout ( As shown in Figure 17 to Figure 26, these two states
  • the layout of the fastening bolts 3 has its own advantages. The appearance of the built-in layout compressor is better handled, and the exposed layout facilitates the installation of the fastening bolts 3. Of course, the structural layout must be determined according to the specific conditions.
  • the term "the slotted hole 4 is located at the end of the motor casing 1 near the main bearing housing 2 of the pump head" as described in the present invention includes the following contents: First, the slot-shaped hole 4 is opened on the motor casing 1 Secondly, the slot-shaped hole 4 is close to the pump main bearing housing 2, that is, the axial direction of the motor rotor 1b.
  • the slot-shaped hole 4 has at least a part of the inner edge 4a located in the middle cross section of the motor casing 1 (ie, the motor casing) 1 cross section at half the axial length) and the end edge 1a of the motor casing 1 (where the end edge 1a is butted against the pump head main bearing 2); and the slotted hole 4 is opposite to the motor casing 1 may be an open groove shape (not shown) or a completely closed hole shape (the groove-shaped hole 4 is kept at a certain axial distance from the end edge 1a of the motor casing 1), see the figure. 1.
  • the optimum structural form is a slotted hole 4
  • the closed hole-shaped structure is not opened with respect to the motor casing 1; the groove-shaped hole 4 has the advantage of being closed-hole-shaped: on the one hand, the first end of the motor casing is not damaged
  • the closed circumference of the lip 1a is annular, thereby ensuring the positioning fit between the motor casing 1 and the main bearing housing 2 of the pump head and maintaining a good hoop fastening force; on the other hand, the handle card 5 and the motor barrel can be made
  • the shell 1 has a better grip on the grip so that the two can bear each other to ensure that the motor casing 1 and the pump head main bearing 2 maintain a stronger mutual tightening force.
  • the present invention adopts a combination form of the handle clip 5 and the slot-shaped hole 4, and at the same time, the fastening bolt 3 can effectively tighten the motor casing 1 and the pump head main bearing seat 2, that is, it can effectively The motor is fastened to the pump head of the compressor. Since the handle clip 5 is relatively close to the pump head main bearing housing 2, the length of the fastening bolt 3 of the present invention can be greatly shortened compared to the conventional practice, as an example.
  • the diameter of the fastening bolt 3 is 5 mm, and the length of the conventional bolt 3 is usually 100 mm to 150 mm (depending on the axial length of the stator 1c of the motor), and the fastening bolt of the present invention only needs to have a length of 20 mm to 25 mm.
  • the positive effect obtained thereby is that on the one hand the torsional rigidity of the fastening bolt 3 is greatly enhanced, in other words The tightening force of the bolt, that is, the tightening torque, can be increased, thereby improving the connection quality between the compressor motor and the pump head.
  • the shorter fastening bolt 3 can save the bolt material and can reduce the assembly difficulty of the bolt, thereby enabling Effectively reduce the production cost of the compressor.
  • the nozzle main bearing block 2 can be provided with a stop structure and a positioning fit with the motor casing 1 , and the first thread on the handle card 5 can be relatively easily obtained.
  • the hole 5a or the first through hole 5b is arranged on the same distributed cylindrical surface as the second through hole 2a or the second threaded hole on the pump head main bearing seat 2, so that the bolt 3 and the thread can be fastened and placed efficiently and conveniently.
  • the "setting of the stop structure on the main bearing housing 2 of the pump head and the positioning of the motor casing 1" includes two cases: the first type In the case where the nozzle of the main bearing housing 2 of the pump head is configured as a convex structure stop 2c, the convex structure stop 2c is positioned and engaged with the inner wall surface of the motor casing 1 (as shown in FIGS. 1 to 26).
  • the second case is that the nozzle of the main bearing housing 2 of the pump head is configured as a concave structure structure (not shown), and the recess of the concave structure is positioned and matched with the outer cylindrical surface of the motor casing 1 .
  • the pump head main bearing housing 2 is provided with a stop structure and a positioning cooperation with the motor casing 1 .
  • the other advantage is that the joint rigidity can be enhanced by using the anchor structure, for example, the motor casing 1 can be fully utilized at the end.
  • the hoop tightness force (when the mouth is configured as the convex structure stop 2c) or the outer support force (when the mouth is configured as a concave structure stop) is generated by the lip 1a and its vicinity to increase the rigidity.
  • Some preferred examples of the contact retaining member 5 of the present invention employing a contact bearing structure are:
  • the handle clip 5 is a separate member, and the handle clip 5 has one end that abuts against the inner edge 4a of the slot-shaped hole 4 and has a first contact point A, while the other end of the handle card 5 rests on the pump head Main bearing housing 2 There is a second contact point B (as shown in FIG. 2, FIG. 4 and FIG.
  • the first threaded hole 5a or the first through hole 5b provided on the handle card member 5 is disposed in a central portion of the handle card member 5;
  • the first threaded hole 5a or the first through hole 5b provided on the handle card member 5 of the present invention is disposed in the central portion of the handle card member 5 to mean an area in which the axis of the motor rotor 1b is taken as an axis After the first cylindrical surface of the first contact point A and the second cylindrical surface passing through the second contact point B with the axis of the motor rotor 1b as the axis, the handle clip 5 falls on the first cylindrical surface and the second cylindrical surface.
  • the area of the inter-fitting is the middle area of the handle card member 5; it should be noted that the handle card 5 laid out in this embodiment is pulled by the fastening bolt 3 when the fastening member 5 is tightened.
  • the first contact point A the pressure of the inner edge 4a of the slot-shaped hole 4 is received, and at the second contact point B, the pressure of the pump head main bearing block 2 is received by the handle contact member 2; in addition, it should be noted that the first cylindrical surface
  • the radius may be greater or smaller than the radius of the second cylindrical surface: when the radius of the first cylindrical surface is greater than the second
  • the optimal layout structure of the fastening bolt 3 is contained by the motor casing 1 (as shown in Figs.
  • the fastening bolt 3 at this time belongs to the built-in layout;
  • the optimal layout structure of the fastening bolt 3 is arranged outside the motor casing 1 (not shown), and the fastening bolt 3 is exposed.
  • the first contact point A and the second contact point B in the present invention are generally referred to as a contact point, a plurality of contact points, or an area contact point ( This region is composed of a collection of a plurality of contact points, and accordingly, there may be a plurality of first cylindrical faces and second cylindrical faces, respectively.
  • the present invention can provide a positioning flange 5c on the handle card 5, the positioning flange 5c is not in the same plane with respect to the main body of the handle card 5, but there is a junction connection between them, that is, positioning.
  • the flange 5c is bent relative to the handle clip 5, and the positioning flange 5c is in contact with the wall surface of the motor casing 1 and is limited by the motor casing 1 (as shown in FIGS. 5 and 6).
  • the positioning flange 5c is in contact with the main bearing housing 2 of the pump head and is limited by the main bearing housing 2 of the pump head (as shown in Figures 3 and 4).
  • the advantage of providing the positioning flange 5c is that the position of the handle card 5 can be pre-positioned during installation, and on the one hand, the first threaded hole 5a or the first through hole 5b has a predetermined radial position or even a certain determination.
  • the circumferential position on the other hand allows the assembly worker to reduce the operation, for example, when tightening the fastening bolt 3, it is not necessary to take into account the tightening action and also to prevent the fastening bolt 3 from falling or moving, thereby improving Assembly efficiency; it should be noted that the positioning flange 5c is in contact with the wall surface of the motor casing 1 including both the positioning flange 5c and the inner surface of the motor casing 1 (not shown) and the positioning flange 5c.
  • the fastening bolt 3 is optimally arranged to be exposed relative to the motor casing 1; in addition, when positioning the flange 5c and the pump head When the bearing housing 2 comes into contact, the contact point can fall
  • the inside of the motor casing 1 (including the inside of the extension cylinder casing that falls on the motor casing 1) may also fall outside the motor casing 1 (including the outside of the extension cylinder casing of the motor casing 1).
  • the fastening bolt 3 is exposed to the motor casing 1 (not shown), and the fastening bolt 3 is inside the motor casing 1 with the fastening bolt 3 inside.
  • Tibetan as shown in Figures 4 and 6).
  • the handle card 5 is a separate piece, and the handle card 5 comprises an "L" type configuration (as shown in Figures 7 to 10), that is, it has two body sides, wherein one side of the handle card 5 and the motor
  • the wall surface of the casing 1 has a contact portion C and becomes a fastening edge 5d.
  • the other side of the handle card 5 passes through the slot-shaped hole 4 in the motor casing 1 to become a radial pull 5e, which is provided by the handle card 5.
  • the first threaded hole 5a or the first through hole 5b is disposed on the radial pull 5e (as shown in FIG. 7 to FIG. 10). It should be noted that the optimal layout of the radial pull 5e is with the motor barrel.
  • the inner edge 4a of the shell 1 which is closer to the side of the main bearing housing 2 of the pump head There is a first contact point A, at which point the fastening force of the fastening bolt 3 received by the handle clip 5 can be directly transmitted to the motor casing 1; in the present invention, the function of the fastening edge 5d is to prevent the radial pull 5e from being Flips when stressed.
  • the present invention can provide a recessed configuration 5f (shown in Figures 9 and 10) on the fastening edge 5d of the handle clip 5, by means of which the buckle can be made
  • the abutting portion C of the tight side 5d and the wall surface of the motor casing 1 is separated from the radial pulling edge 5e by a certain distance, thereby obtaining a larger anti-turning force arm to improve the anti-overturning capability.
  • the fastening edge 5d is in contact with the wall surface of the motor casing 1 including both the fastening edge 5d and the inner surface of the motor casing 1 (not shown), and the fastening edge 5d and the motor cylinder.
  • the outer surface of the shell 1 is in contact (as shown in FIGS. 7 to 10), and if the fastening edge 5d comes into contact with the outer surface of the motor casing 1, the fastening bolt 3 is built-in with respect to the motor casing 1 if When the fastening edge 5d comes into contact with the inner surface of the motor casing 1, the fastening bolt 3 is exposed to the motor casing 1.
  • the handle card 5 is a separate piece, and the handle card 5 comprises a "U"-shaped configuration (as shown in Figures 11 to 16).
  • the middle portion of the handle card 5 is the contact edge 5g and the two ends of the handle card. 5g is bent toward the same side with respect to the contact side and respectively constitutes a radial pull edge 5e and a limit constraint edge 5h, wherein the limit constraint edge 5h which is closer to the main bearing housing 2 of the pump head can be arranged.
  • a radial pulling edge 5e Far from the main bearing housing 2 of the pump head is a radial pulling edge 5e (as shown in Figures 11 to 16), and it is also possible to arrange a radial pulling edge 5e closer to the main bearing housing 2 of the pump head and away from the pump head.
  • the main bearing housing 2 is far from the limit constraint edge 5h (not shown).
  • the best case is that the limit constraint edge 5h is closer to the main bearing housing 2 of the pump head and is closer to the main bearing housing 2 of the pump head.
  • the radial pull 5e and the limit constraining edge 5h both pass through the slotted hole 4 on the motor casing 1, the first threaded hole 5a of the handle clip 5 or the set A through hole 5b is arranged on the radial pulling edge 5e or/and the limiting constraint edge 5h; the purpose of providing the radial pulling edge 5e is to receive the fastening bolt 3
  • the fastening force is transmitted to the inner edge 4a of the slot-shaped hole 4, and the purpose of setting the limit constraint edge 5h is to prevent the handle card 5 from being swayed and flipped during installation, and at the same time, can help the positioning
  • the position of a threaded hole 5a or the first through hole 5b finally facilitates quick and reliable installation of the operation fastening
  • the handle card When the "U" type opening is outwardly arranged, the handle card is opened.
  • the best case of the member 5 is that the contact side 5g is disposed inside the motor casing 1 and the first threaded hole 5a or the first through hole 5b is disposed outside the motor casing 1, and the handle is opened when the "U"-shaped opening faces inward.
  • the best case of the card member 5 is that the contact edge 5g is disposed outside the motor casing 1 and the first threaded hole 5a or the first through hole 5b is disposed within the motor casing 1 for the purpose of considering the handle card.
  • Piece 5 has a better bearing state and a better mounting position.
  • the handle card member 5 of the present invention can be provided with a positioning boss structure 5i (not shown) on its radial pulling edge 5e alone, or a positioning boss structure 5i can be separately provided on its limit constraint side 5h (such as FIG. 15 and FIG. 16), it is also possible to simultaneously provide a positioning boss structure 5i (not shown) on the radial pulling edge 5e and the limiting constraint edge 5h, by which the positioning boss 5i can be better.
  • the ground helps to position the handle clip 5 in order to install the fastening bolt 3 more quickly and accurately.
  • the radial pull 5e and the limit restraining edge 5h of the handle clip 5 of the present invention can pass through the same slotted hole 4 on the motor casing 1 (as shown in Figs.
  • the contact card 5 can be easily positioned by the cross-bar erecting the contact edge 5g (not shown) Show); when radial pull When the 5e and the limit constraint edge 5h respectively pass through two mutually different groove-shaped holes 4, the advantages are as follows: 1) The contact edge 5g can be defined by the wall surface of the motor casing 1 to prevent the handle card 5 from being removed The action of swaying and flipping occurs, 2) the contact edge 5g can be defined by the wall surface of the motor casing 1, whereby the first threaded hole 5a or/and the first through hole 5b can be accurately positioned, thereby facilitating assembly of the fastening bolt 3; when the radial pulling edge 5e and the limiting constraint edge 5h respectively pass through two mutually independent groove-shaped holes 4, if the "U"-shaped opening of the handle card member 5 faces outward, the contact edge 5g is laid out in the motor tube Within the casing 1, if the "U"-shaped opening of the handle card member 5 faces inward, the contact edge 5g
  • a preferred example of the hook member 5 of the present invention employing a hook-bearing structure is:
  • the handle card member 5 is a separate member, and a hook-shaped structure 5j is disposed on the handle card member 5 to be hooked on the inner edge 4a of the slotted hole 4 of the motor casing 1 (as shown in FIGS. 17 and 18); It should be noted that the hook-shaped structure 5j can be hooked from the outer side to the inner edge 4a of the slotted hole 4 of the motor casing 1 (as shown in FIGS. 17 and 18), or can be hooked from the inside to the outside.
  • the hook-shaped structure 5j is hooked outwardly from the inner edge 4a of the slotted hole 4 of the motor casing 1
  • the main body of the handle card 5 is outside the motor casing 1 , and when the hook structure 5 j is hooked from the inside to the outside on the inner edge 4 a of the slotted hole 4 of the motor casing 1 , the handle clip The main body of 5 is inside the motor casing 1; in addition, a certain axial gap is maintained between the handle card 5 and the main bearing housing 2 of the pump head to facilitate reliable fastening of the motor, obviously when the hooking structure is used 5 installation is faster.
  • Some preferred examples of the handle member 5 of the present invention employing a snap-fit bearing structure are:
  • the handle clip 5 is a separate piece and is snapped into the slotted hole 4 of the motor casing (not shown), or
  • the handle card 5 and the motor casing 1 are made of an integral member and are punched into a curved arch shape when punching the slotted hole 4 of the motor casing (as shown in FIGS. 19 and 20); when the handle card 5 is In the case of a separate piece, the handle clip 5 is snapped onto the inner edge 4a of the slotted hole 4 of the motor casing 1, and the handle clip 5 and the slotted hole 4 can be either loose or tight.
  • a first through hole 5b (not shown) is formed to fit the fastening bolt 3; it should be noted that the arcuate arch can be directed to the inside of the motor casing 1
  • the recess (not shown) can also be raised to the outside of the motor casing 1 (as shown in Figs. 19 and 20); it should be noted that the handle card 5 When the bearing structure is engaged with the card, the first threaded hole 5a (as shown in FIG. 19 and FIG. 20) or the first through hole 5b (not shown) may be opened on the handle card 5, and the handle card is additionally provided. Maintaining a certain axial clearance between the piece 5 and the main bearing housing 2 of the pump head will facilitate reliable fastening of the motor.
  • the structure of the handle card 5 can be made relatively simple when the snap-fit structure is used.
  • Some preferred examples of the handle member 5 of the present invention employing a connected load bearing structure are:
  • the handle card 5 and the motor casing 1 are integral members, and the handle card 5 is formed by bending and bending the residual material formed by the slotted hole 4 of the motor casing 1 (see FIGS. 21 to 24).
  • the first threaded hole 5a can be disposed on the handle card 5 (as shown in FIG. 21 and FIG. 22), or the first through hole 5b can be opened on the handle card 5 (as shown in FIG. 23 to FIG. 23). 24); obviously, when the first through hole 5b is opened in the handle card 5 and the second through hole 2a is also formed in the main bearing housing 2 of the pump head, the nut 6 can be used to fasten the motor casing 1 (such as Figures 23 and 24), and in turn the motor can be tightened.
  • a certain reinforcing flange structure 5k is arranged on the handle card 5 (as shown in FIG. 21 to FIG. 24), wherein the optimal structure of the reinforcing flange structure 5k is longitudinally distributed along the axial direction of the motor and has a certain The radial thickness, and the reinforced flange forming structure 5k, preferably comes into contact with the wall surface of the motor casing 1.
  • a preferred example of the first through-hole 5b of the open-handed card member 5 of the present invention is:
  • the first through hole 5b opened in the handle card member 5 has an open groove-like structure (as shown in FIGS. 25 and 26), and this form facilitates quick installation of the fastening bolt 3.
  • a preferred example of the second main through-hole 2a of the pump head main bearing housing 2 of the present invention is:
  • the second through hole 2a formed in the main bearing housing 2 of the pump head has an open groove-like structure (not shown), and this form facilitates quick installation of the fastening bolt 3.
  • the present invention has a significant advantage over the prior art in that the length of the fastening bolt 3 is greatly shortened by providing a handle clip 5 close to the pump head main bearing housing 2 to fasten the structure of the motor casing 1
  • the torsional rigidity of the fastening bolt 3 is improved, thereby improving the connection quality between the compressor motor and the pump head, and on the other hand, the bolt material is saved and the assembly difficulty of the bolt is reduced, so that the production cost of the compressor can be effectively reduced.

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  • Engineering & Computer Science (AREA)
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Abstract

一种直联式空气压缩机电机的紧固连接结构，电机筒壳（1）上靠近泵头主轴承座（2）的一端成型有槽形孔洞（4），另外设置有与该槽形孔洞（4）作承力配合的拉手卡件（5），拉手卡件（5）上设置有第一螺纹孔（5a）或/和第一穿通孔（5b），泵头主轴承座（2）上设置有第二螺纹孔或/和第二穿通孔（2a），紧固螺栓（3）穿越第二穿通孔（2a）与第一螺纹孔（5a）进行连接，或者穿越第一穿通孔（5b）与第二螺纹孔进行连接，或者穿越第二穿通孔（2a）及第一穿通孔（5b）与螺帽（6）进行连接，从而将电机筒壳（1）紧固到泵头主轴承座（2）上。由于紧固螺栓（3）的长度大大缩短，一方面增强了紧固螺栓（3）的扭转刚度而提高了电机与泵头的连接质量，另一方面节约了螺栓材料并降低了螺栓的装配难度，从而降低了压缩机的生产成本。

Description

直联式空气压缩机电机紧固连接结构 技术领域
本发明属于压缩机技术领域，涉及一种空气压缩机电机的紧固连接结构，具体地说涉及一种采用电机直接驱动压缩机泵头运转的直联式空气压缩机其电机与泵头本体之间相互紧固连接的结构。
背景技术
直联式空气压缩机是一种量大面广的机电产品，被广泛应用于装修装饰、医疗保健、电子封装和食品包装等行业。直联式空气压缩机顾名思义是其电机直接连接并驱动压缩机泵头的空气压缩机，由于采用直接驱动的方式，因此直联式压缩机的转速相对较高；也因此，该类压缩机的整机体积相比于那些非直联式的压缩机来说(比如皮带驱动型的空气压缩机)可以做得更加轻便和小巧。直联式空气压缩机包括电机和泵头两大组成部分，其中泵头包括气缸、活塞、连杆、曲轴和主轴承座等零部件，电机的转子直接驱动曲轴及活塞连杆组件运转、或者电机的转子轴干脆就是泵头曲轴的本体而直接驱动活塞连杆组件运转。众所周知，凡直联式空气压缩机其电机必须紧固连接到压缩机的泵头上，现有的紧固做法均是采用若干(通常为四根)长度超过压缩机定子长度的长螺栓将电机紧固到泵头的主轴承座上，这些螺栓环布并紧邻在电机定子的四周且轴向贯通或者跨越定子，以此从轴向方向将电机的定子或者将电机的外筒壳拉紧贴靠在主轴承座上，从而实现紧固电机的目的。
很显然，直联式空气压缩机的传统电机紧固结构存在有若干不足，主要表现在：1)采用长螺栓的紧固构件形式使得电机的紧固质量难以保证，由于所用紧固螺栓的长径比通常达到二十比一以上，属于典型的超长细杆结构，以至于 螺栓的扭转刚度难以承受更大的紧固力矩，所以紧固螺栓的紧固力往往较小；众所周知，直联式空气压缩机的转速非常之高，其振动频率远高于其他类型的往复式压缩机，加之直联式压缩机电机的配装常常为一端自由另一端紧固的悬臂结构支承(至少对产量最大的单缸空气压缩机来说是如此布局)，而小的紧固力矩很容易造成螺栓紧固失效而最终导致电机松脱，换言之长螺栓紧固电机的结构方式其紧固质量较差。2)采用长螺栓的紧固构件形式使得压缩机整机生产成本上升，首先较长的长度必然增加螺栓的材料成本，其次较长的螺栓必然增加制作成本：一方面长螺栓不易在安装时对准安装孔，尤其是电机设置有外筒壳并利用外筒壳与泵头主轴承座进行定位的情况下，长螺栓常常从电机筒壳内穿越并与泵头主轴承座的螺纹孔配接，此时的紧固动作为盲视操作模式，其就位难度之高不难想象，由此造成生产效率降低并进而增加人工成本；另一方面由于长螺栓必然增大重量和体积，由此派生出更多的搬运成本及仓储成本，这些成本不仅发生在生产制作过程，而且还发生在装箱货运尤其是在出口货运的过程，虽然上述成本的增加对于单台压缩机产品来说微不足道，但是注意到直联式空气压缩机通常都是大批量生产的产品，积沙成塔的效应就会突显出可观的额外成本。
发明内容
针对目前直联式空气压缩机电机紧固连接结构所存在的上述问题，本发明提出一种直联式空气压缩机电机紧固连接结构，目的在于通过改进和更新传统的紧固结构以提高压缩机电机与泵头之间的连接质量，并有效降低压缩机的生产成本。
本发明的目的是这样来实现的：直联式空气压缩机电机紧固连接结构，包 括电机筒壳、泵头主轴承座和紧固螺栓，其特征在于：在电机筒壳上成型有槽形孔洞，所述槽形孔洞位于电机筒壳靠近泵头主轴承座的一端，另外设置有与该槽形孔洞相呼应的拉手卡件，其中相互组配的拉手卡件和槽形孔洞之间存在相互承力的关系，电机筒壳与泵头主轴承座相互紧固连接的结构包含有以下三种情形之一：a)在拉手卡件上设置有第一螺纹孔、同时在泵头主轴承座上设置有与之呼应的第二穿通孔，所述紧固螺栓穿越第二穿通孔并与第一螺纹孔进行螺纹连接而将电机筒壳与泵头主轴承座相互拉紧；b)在拉手卡件上设置有第一穿通孔、同时在泵头主轴承座上设置有与之呼应的第二螺纹孔，所述紧固螺栓穿越第一穿通孔并与第二螺纹孔进行螺纹连接而将电机筒壳与泵头主轴承座相互拉紧；c)在拉手卡件上设置有第一穿通孔、同时在泵头主轴承座上设置有与之呼应的第二穿通孔，所述紧固螺栓穿越第二穿通孔及第一穿通孔并与螺帽进行螺纹连接而将电机筒壳与泵头主轴承座相互拉紧。
上述的泵头主轴承座上设置有止口构造与电机筒壳作定位配合。
上述拉手卡件为独立构件，并且该拉手卡件有一端搭靠在槽形孔洞的内缘边上、同时拉手卡件另有一端搭靠在泵头主轴承座上，拉手卡件上设置的第一螺纹孔或第一穿通孔布局在拉手卡件的中部区域。
上述拉手卡件设置有定位折边，该定位折边与电机筒壳的壁面发生接触并受到电机筒壳的限位、或者该定位折边与泵头主轴承座发生接触并受到泵头主轴承座的限位。
上述拉手卡件为独立件并包含有“L”型构造，该拉手卡件的一边与电机筒壳的壁面存在有贴靠部位而成为扣紧边、拉手卡件的另一边穿越电机筒壳上的槽形孔洞而成为径向拉边，拉手卡件设置的第一螺纹孔或第一穿通孔布局在径 向拉边上。
上述拉手卡件的扣紧边设置有沉凹构造并借助该沉凹构造使该扣紧边与电机筒壳壁面的贴靠部位远离径向拉边一定距离。
上述拉手卡件为独立件并包含有“U”型构造，该拉手卡件的中间部位为联系边、拉手卡件的两端相对于联系边朝同一侧向进行弯折并分别构成径向拉边和限位约束边，所述径向拉边及限位约束边均穿越电机筒壳上的槽形孔洞，拉手卡件设置的第一螺纹孔或第一穿通孔布局在径向拉边或/和限位约束边上。
上述拉手卡件的径向拉边或/和限位约束边上设置有定位凸台构造。
上述拉手卡件的径向拉边和限位约束边分别穿越电机筒壳上的两个相互独立的槽形孔洞。
上述拉手卡件为独立件，并且该拉手卡件设置有钩形结构，所述钩形结构勾接在电机筒壳槽形孔洞的内缘边上。
上述拉手卡件为独立件并卡接在电机筒壳的槽形孔洞内、或者拉手卡件与电机筒壳为一体构件制作并且由冲制电机筒壳槽形孔洞时冲制成弧形拱状。
上述拉手卡件与电机筒壳为一体构件，并且该拉手卡件由冲制电机筒壳槽形孔洞所形成的余料实行翻边弯折而成。
上述拉手卡件有加强翻边构造。
上述拉手卡件上开设的第一穿通孔为开口槽状的结构形式。
上述泵头主轴承座上开设的第二穿通孔为开口槽状的结构形式。
本发明相比现有技术具有的突出优点是：通过在靠近泵头主轴承座设置拉手卡件扣紧电机筒壳的结构，使得紧固螺栓的长度大大缩短，一方面大大增强了紧固螺栓的扭转刚度，从而可以承受更大的紧固力，籍此可有效提高压缩机 电机与泵头之间的连接质量，另一方面采用短的螺栓连接不仅节约了所用螺栓的材料，而且还可降低螺栓的装配难度，从而可以有效降低压缩机的生产成本。
附图说明
图1是本发明直联式空气压缩机电机紧固连接结构包含有两端接触承力式拉手卡件实施例的装配爆炸示意图；
图2是图1所示实施例的装配轴测及局部装配剖视示意图；
图3是本发明直联式空气压缩机电机紧固连接结构包含有定位折边的两端接触承力拉手卡件实施例的装配爆炸示意图；
图4是图3所示实施例的装配轴测及局部装配剖视示意图；
图5是本发明直联式空气压缩机电机紧固连接结构包含有定位折边的两端接触承力拉手卡件的另一个实施例的装配爆炸示意图；
图6是图5所示实施例的装配轴测及局部装配剖视示意图；
图7是本发明直联式空气压缩机电机紧固连接结构包含有“L”型拉手卡件实施例的装配爆炸示意图；
图8是图7所示实施例的装配轴测及局部装配剖视示意图；
图9是本发明直联式空气压缩机电机紧固连接结构包含有附带沉凹构造的“L”型拉手卡件实施例的装配爆炸示意图；
图10是图9所示实施例的装配轴测及局部装配剖视示意图；
图11是本发明直联式空气压缩机电机紧固连接结构包含有“U”型拉手卡件并每个拉手卡件仅匹配一个槽形孔洞实施例的装配爆炸示意图；
图12是图11所示实施例的装配轴测及局部装配剖视示意图；
图13是本发明直联式空气压缩机电机紧固连接结构包含有“U”型拉手卡 件并每个拉手卡件匹配两个槽形孔洞实施例的装配爆炸示意图；
图14是图13所示实施例的装配轴测及局部装配剖视示意图；
图15是本发明直联式空气压缩机电机紧固连接结构包含有“U”型拉手卡件并设置有定位凸台构造的实施例的装配爆炸示意图；
图16是图15所示实施例的装配轴测及局部装配剖视示意图；
图17是本发明直联式空气压缩机电机紧固连接结构包含有勾接型拉手卡件的实施例的装配爆炸示意图；
图18是图17所示实施例的装配轴测及局部装配剖视示意图；
图19是本发明直联式空气压缩机电机紧固连接结构包含有与电机筒壳一体制作的卡接型拉手卡件的实施例的装配爆炸示意图；
图20是图19所示实施例的装配轴测及局部装配剖视示意图；
图21是本发明直联式空气压缩机电机紧固连接结构包含有与电机筒壳一体制作的拉手卡件的实施例的装配爆炸示意图；
图22是图21所示实施例的装配轴测及局部装配剖视示意图；
图23是本发明直联式空气压缩机电机紧固连接结构包含有与电机筒壳一体制作并配置螺母的拉手卡件的实施例的装配爆炸示意图；
图24是图23所示实施例的装配轴测及局部装配剖视示意图；
图25是本发明直联式空气压缩机电机紧固连接结构包含有开口槽状穿通孔的拉手卡件的实施例的装配爆炸示意图；
图26是图25所示实施例的装配轴测及局部装配剖视示意图。
具体实施方式
下面以具体实施例对本发明作进一步描述，参见图1-26：
直联式空气压缩机电机紧固连接结构，包括电机筒壳1、泵头主轴承座2和紧固螺栓3，其中电机定子1c安置在电机筒壳1的内部并与之紧固配合、电机转子1b(包括其转轴)被支承在泵头主轴承座2的轴承上、电机转子1b上紧固有曲轴或者电机转子1b与曲轴为一体制作、由电机转子1b直接驱动压缩机的连杆并进而驱动活塞进行运转；区别于传统压缩机电机连接结构中所用紧固螺栓3为长螺栓结构的状况(此时紧固螺栓3的长度超过电机定子1c的长度)，本发明所用紧固螺栓3的长度为远远短于电机定子1c长度的短螺栓，为此：本发明在电机筒壳1上成型有槽形孔洞4，所述槽形孔洞4位于电机筒壳1靠近泵头主轴承座2的一端(或者说电机筒壳1的两端头中有一端与泵头主轴承座2进行紧固配合，本发明中的槽形孔洞4即开设在与泵头主轴承座2做紧固连接的这一端的电机筒壳1上)，另外设置有与该槽形孔洞4相呼应的拉手卡件5，其中相互组配(即有相互关联相互配合关系的一对)的拉手卡件5和槽形孔洞4之间存在相互承力的关系，亦即拉手卡件5与槽形孔洞4存在接触承力(当拉手卡件5为独立构件时)或者拉手卡件5与槽形孔洞4存在本体相连承力(当拉手卡件5与电机筒壳1为一体结构制作时)的关系，此时将电机筒壳1紧固到泵头主轴承座2时在拉手卡件5与槽形孔洞4之间存在有相互作用的力，或者说拉手卡件5与槽形孔洞4通过相互接触或者相互相连来承受和传递紧固螺栓3的作用力；本发明的电机筒壳1与泵头主轴承座2相互紧固连接的结构包含有以下三种情形之一：a)在拉手卡件5上设置有第一螺纹孔5a、同时在泵头主轴承座2上设置有与之相呼应的第二穿通孔2a，所述紧固螺栓3穿越该第二穿通孔2a并与所呼应的第一螺纹孔5a进行螺纹连接而将电机筒壳1与泵头主轴承座2相互拉紧(如图1至图22所示)；b)在拉手卡件5上设置有第一穿通 孔5b、同时在泵头主轴承座2上设置有与之相呼应的第二螺纹孔，所述紧固螺栓3穿越该第一穿通孔5b并与所呼应的第二螺纹孔进行螺纹连接而将电机筒壳1与泵头主轴承座2相互拉紧(图中未示出)；c)在拉手卡件5上设置有第一穿通孔5b、同时在泵头主轴承座2上设置有与之相呼应的第二穿通孔2a，所述紧固螺栓3穿越该第二穿通孔2a及该第一穿通孔5b并与螺帽6进行螺纹连接而将电机筒壳1与泵头主轴承座2相互拉紧(如图23至图26所示)。在这里需要说明的是，当采用有螺帽6结构时，本发明包括以下两种情形：第一种情形是螺帽6布局在电机筒壳1的这一侧，此时紧固螺栓3将首先穿越第二穿通孔2a接着穿越第一穿通孔5b然后再与螺帽6进行螺纹连接(如图23至图26所示)；第二种情形是螺帽6布局在泵头主轴承座2的这一侧，此时紧固螺栓3将首先穿越第一穿通孔5b接着穿越第二穿通孔2a然后再与螺帽6进行螺纹连接(图中未示出)；另外螺帽6既可以是常规的标准件也可以是特制的非标件、既可以直接与拉手卡件5或与泵头主轴承座2进行配合也可以通过其它垫片间接与它们进行配合。特别需要指出的是，本发明中所说的电机筒壳1与泵头主轴承座2相互紧固连接的结构，既包括仅涉及采用上述三种紧固结构中的一种、也包括同时涉及采用上述三种紧固结构中的两种或者三种(即采用它们的各种组合)、还包括至少采用上述三种紧固结构中的一种并配合其它紧固结构，换句话说只要存在上述三种紧固结构中的一种即属于本发明的范畴。另外需要指出的是，本发明中所涉及的紧固螺栓3既可以布局在电机筒壳1之内也可以布局在电机筒壳1之外，即既可以让紧固螺栓3被电机筒壳1环抱在其内孔壁以内而成为内藏式螺栓布局(如图1至图16所示)、也可以让紧固螺栓3布置在电机筒壳1的外圆柱表面以外而成为外露式螺栓布局(如图17至图26所示)，这两种状态 的紧固螺栓3布局各有千秋，内藏式布局压缩机的外观较好处置、外露式布局则方便安装紧固螺栓3，当然采用那种结构布局须根据具体情况来确定。还需要指出的是，本发明中所说的“槽形孔洞4位于电机筒壳1靠近泵头主轴承座2的一端”包含有如下内容：首先槽形孔洞4开设在电机筒壳1上，其次槽形孔洞4靠近泵头主轴承座2，亦即指按电机转子1b的轴向进行考察，槽形孔洞4至少存在部分内缘边4a位于电机筒壳1中间横断面(即电机筒壳1轴向长度一半处的横断面)与电机筒壳1端头口缘1a之间(其中该端头口缘1a与泵头主轴承座2对接)；另外槽形孔洞4相对于电机筒壳1可以为开口槽状(图中未示出)、也可以为完整闭合的孔洞状(此时槽形孔洞4距电机筒壳1的端头口缘1a保留有一定的轴向距离，参见图1、图3、图5、图7、图9、图11、图13、图15、图17、图19、图21、图23和图25)，其中最佳的结构形式为槽形孔洞4相对于电机筒壳1为不开通的闭合孔洞状结构；槽形孔洞4为闭合孔洞状的优点是：一方面不破坏电机筒壳1端头口缘1a的闭合圆周环状，从而保证电机筒壳1与泵头主轴承座2之间的定位配合并保持有较好的环抱紧固力；另一方面可以使拉手卡件5与电机筒壳1有一个更好的着力抓手，以便两者能够相互承力以保证电机筒壳1与泵头主轴承座2保持更强的相互拉紧的紧固力。显然，本发明采用拉手卡件5结合槽形孔洞4的组合形式，同时辅以紧固螺栓3即可以有效地将电机筒壳1与泵头主轴承座2相互拉紧，亦即能够有效将电机紧固到压缩机的泵头之上，由于拉手卡件5距离泵头主轴承座2比较近，因此本发明的紧固螺栓3的长度相比传统做法可以大大缩短，以一个例子为说明：设紧固螺栓3的直径为5mm，则传统螺栓3的长度通常在100mm至150mm(视电机定子1c的轴向长度而定)，而本发明的紧固螺栓只需长度20mm至25mm即可完成 同样的紧固功能而且紧固效果更好(并且与电机定子1c的轴向长度基本上无关)，由此获得的积极效果是，一方面大大增强了紧固螺栓3的扭转刚度，换言之籍此可以加大螺栓的紧固力即紧固力矩，进而可以提高压缩机电机与泵头的连接质量，另一方面较短的紧固螺栓3可以节约螺栓材料并可以降低螺栓的装配难度，从而能够有效降低压缩机的生产成本。
本发明为了更加高效地装配紧固螺栓3，可以在泵头主轴承座2上设置止口构造与电机筒壳1作定位配合，此时可以比较容易地让拉手卡件5上的第一螺纹孔5a或第一穿通孔5b与泵头主轴承座2上的第二穿通孔2a或第二螺纹孔安排在同一分布圆柱面上，如此能够高效便捷地就位紧固螺栓3与上述螺纹及穿通孔之间的相对位置，从而有利于提高装配效率；本发明所说的“在泵头主轴承座2上设置止口构造与电机筒壳1作定位配合”包括两种情形：第一种情形是泵头主轴承座2的止口构造为凸状结构止口2c，此时该凸状结构止口2c与电机筒壳1的内壁面作定位配合(如图1至图26所示)；第二种情形是泵头主轴承座2的止口构造为沉凹状结构止口(图中未示出)，此时该沉凹状结构止口与电机筒壳1的外圆柱面作定位配合。另外，泵头主轴承座2设置止口构造与电机筒壳1作定位配合还有一个好处就是，可以利用止口结构加强它们之间的配合刚度，比如可以充分发挥电机筒壳1位于端头口缘1a及其附近部位产生的环抱紧箍力(当止口构造为凸状结构止口2c时)或者外撑力(当止口构造为沉凹状结构止口时)来提高刚性。
本发明拉手卡件5采用接触承力结构的若干优选例是：
拉手卡件5为独立构件，并且该拉手卡件5有一端搭靠在槽形孔洞4的内缘边4a上并有第一接触点A、同时拉手卡件5另有一端搭靠在泵头主轴承座2 上并有第二接触点B(如图2、图4和图6所示)，拉手卡件5上设置的第一螺纹孔5a或第一穿通孔5b布局在拉手卡件5的中部区域；其中，本发明所说的拉手卡件5上所设置的第一螺纹孔5a或第一穿通孔5b布局在拉手卡件5的中部区域是指这么一个区域：以电机转子1b的轴线为轴线作经过第一接触点A的第一圆柱面、以电机转子1b轴线为轴线作经过第二接触点B的第二圆柱面，则拉手卡件5上落在第一圆柱面与第二圆柱面之间围构的区域即为所指拉手卡件5的中部区域；需要说明的是，按本实施例布局的拉手卡件5，当其受到紧固螺栓3紧固作用力时，拉手卡件5在第一接触点A受到槽形孔洞4内缘边4a的压力、同时拉手卡件5在第二接触点B受到泵头主轴承座2的压力；另外需要说明的是，第一圆柱面的半径既可以大于也可以小于第二圆柱面的半径：当第一圆柱面的半径大于第二圆柱面的半径时，紧固螺栓3的最佳布局结构为其被电机筒壳1包容(如图2和图4所示)，此时的紧固螺栓3属于内藏式布局；而当第一圆柱面的半径小于第二圆柱面的半径时，紧固螺栓3的最佳布局结构为其布置在电机筒壳1的外面(图中未示出)，此时紧固螺栓3属于外露式布局；还需要说明的是，本发明中所说的第一接触点A和第二接触点B乃是泛指，它可以是一个接触点也可以是若干接触点还可以是一个区域接触点(该区域由众多接触点的集合而构成)，因此相应地第一圆柱面和第二圆柱面也可以各有多个。为了在装配时更加便利，本发明可以在拉手卡件5上设置定位折边5c，所述定位折边5c相对于拉手卡件5的主体不在同一平面但它们之间有交汇连接，亦即定位折边5c相对于拉手卡件5有弯折的情形，另外该定位折边5c与电机筒壳1的壁面发生接触并受到电机筒壳1的限位(如图5和图6所示)、或者该定位折边5c与泵头主轴承座2发生接触并受到泵头主轴承座2的限位(如图3和图4所 示)；设置定位折边5c的好处是可以在安装时预先定位拉手卡件5的位置，一方面让其第一螺纹孔5a或第一穿通孔5b有一个预先确定的径向位置甚至有确定的周向位置，另一方面可以让装配工人减少操作动作、比如说可以在拧紧紧固螺栓3时不用既要顾及拧紧动作又要顾及不让紧固螺栓3掉落或走位，因此可以提高装配效率；需要说明的是，定位折边5c与电机筒壳1的壁面发生接触既包括定位折边5c与电机筒壳1的内表面发生接触(图中未示出)也包括定位折边5c与电机筒壳1的外表面发生接触(如图5和图6所示)，若定位折边5c与电机筒壳1的外表面发生接触则紧固螺栓3最佳布局为相对于电机筒壳1为内藏式，若定位折边5c与电机筒壳1的内表面发生接触则紧固螺栓3最佳布局为相对于电机筒壳1为外露式；另外当定位折边5c与泵头主轴承座2发生接触时，其接触点既可以落在电机筒壳1的里面(包括落在电机筒壳1的延长筒壳体的里面)也可以落在电机筒壳1的外面(包括落在电机筒壳1的延长筒壳体的外面)，落在电机筒壳1的外面则紧固螺栓3相对于电机筒壳1为外露式(图中未示出)、落在电机筒壳1的里面则紧固螺栓3相对于电机筒壳1为内藏式(如图4和图6所示)。
本发明拉手卡件5采用“L”型构造结构的若干优选例是：
拉手卡件5为独立件，并且该拉手卡件5包含有“L”型构造(如图7至图10所示)，亦即它有两条主体边，其中拉手卡件5的一边与电机筒壳1的壁面存在有贴靠部位C而成为扣紧边5d、拉手卡件5的另一边穿越电机筒壳1上的槽形孔洞4而成为径向拉边5e，拉手卡件5设置的第一螺纹孔5a或者设置的第一穿通孔5b布局在径向拉边5e上(如图7至图10所示)，需要说明的是，径向拉边5e的最佳布局是与电机筒壳1中较为靠近泵头主轴承座2一侧的内缘边4a 存在第一接触点A，此时可以将拉手卡件5受到的紧固螺栓3的紧固力直接传递给电机筒壳1；本发明中扣紧边5d的功用是防止径向拉边5e在受力时发生翻转。为了能够获得更好的防翻转效果，本发明可以在拉手卡件5的扣紧边5d上设置沉凹构造5f(如图9和图10所示)，借助该沉凹构造5f可使该扣紧边5d与电机筒壳1壁面的贴靠部位C远离径向拉边5e一定距离，以此获得更大的防翻转力臂从而提高防翻转能力。需要说明的是，扣紧边5d与电机筒壳1的壁面发生接触既包括扣紧边5d与电机筒壳1的内表面发生接触(图中未示出)也包括扣紧边5d与电机筒壳1的外表面发生接触(如图7至图10所示)，若扣紧边5d与电机筒壳1的外表面发生接触则紧固螺栓3相对于电机筒壳1为内藏式，若扣紧边5d与电机筒壳1的内表面发生接触则紧固螺栓3相对于电机筒壳1为外露式。
本发明拉手卡件5采用“U”型构造结构的若干优选例是：
拉手卡件5为独立件，并且该拉手卡件5包含有“U”型构造(如图11至图16所示)，拉手卡件5的中间部位为联系边5g、拉手卡件的两端相对于该联系边5g朝同一个侧向进行弯折并分别构成径向拉边5e和限位约束边5h，其中既可以安排离泵头主轴承座2较近的为限位约束边5h而离泵头主轴承座2较远的为径向拉边5e(如图11至图16所示)，也可以安排离泵头主轴承座2较近的为径向拉边5e而离泵头主轴承座2较远的为限位约束边5h(图中未示出)，最佳情形是离泵头主轴承座2较近的为限位约束边5h而离泵头主轴承座2较远的为径向拉边5e，所述径向拉边5e及限位约束边5h均穿越电机筒壳1上的槽形孔洞4，拉手卡件5设置的第一螺纹孔5a或者设置的第一穿通孔5b布局在径向拉边5e或/和限位约束边5h上；设置径向拉边5e的目的是承接紧固螺栓3的 紧固力并将该紧固力传导至槽形孔洞4的内缘边4a上，设置限位约束边5h的目的是可以防止安装时拉手卡件5发生窜动和翻转、同时可以帮助定位第一螺纹孔5a或第一穿通孔5b的位置，最终有利于快捷并可靠地安装操作紧固螺栓3；需要说明的是，本发明中呈“U”型构造的拉手卡件5其“U”型开口按电机筒壳1的半径方向既可以朝外布局(图中未示出)也可以朝内布局(如图11至图16所示)，当“U”型开口朝外布局时拉手卡件5的最佳情形是其联系边5g布局在电机筒壳1以内而其第一螺纹孔5a或第一穿通孔5b布局在电机筒壳1以外，当“U”型开口朝内布局时拉手卡件5的最佳情形是其联系边5g布局在电机筒壳1以外而其第一螺纹孔5a或第一穿通孔5b布局在电机筒壳1以内，这样做的目的主要是考虑让拉手卡件5具有更好的承力状态和更好的安装位置。本发明的拉手卡件5可以单独在其径向拉边5e上设置定位凸台构造5i(图中未示出)、也可以单独在其限位约束边5h上设置定位凸台构造5i(如图15和图16所示)、还可以同时在其径向拉边5e和限位约束边5h上设置定位凸台构造5i(图中未示出)，利用该定位凸台构造5i能够更好地帮助定位拉手卡件5，以便更加快捷准确地安装紧固螺栓3。本发明的拉手卡件5的径向拉边5e和限位约束边5h既可以穿越电机筒壳1上的同一个槽形孔洞4(如图11、图12、图15和图16所示)也可以分别穿越电机筒壳1上的两个相互独立的槽形孔洞4(如图13和图14所示)；当采用径向拉边5e和限位约束边5h穿越电机筒壳1上同一个槽形孔洞4时：特别适合那些拉手卡件5的“U”型开口朝外布局的情形(图中未示出)，此时比较方便操作安装紧固螺栓3，另外对于“U”型开口朝里布局的情形也可以辅以横杆穿越“U”型开口而假设在电机筒壳1的外表面上，此时借助横杆架设联系边5g即可以轻松定位拉手卡件5(图中未示出)；当径向拉边 5e和限位约束边5h分别穿越两个相互独立的不同槽形孔洞4时，其带来的好处是：1)可以借助电机筒壳1的壁面限定联系边5g，以此防止拉手卡件5出现窜动和翻转的动作，2)可以借助电机筒壳1的壁面来限定联系边5g，借此能够准确定位第一螺纹孔5a或/和第一穿通孔5b，从而有利于装配紧固螺栓3；当径向拉边5e和限位约束边5h分别穿越两个相互独立的槽形孔洞4时，若拉手卡件5的“U”型开口朝外则其联系边5g被布局在电机筒壳1以内，若拉手卡件5的“U”型开口朝内则其联系边5g被布局在电机筒壳1以外；需要说明的是，无论“U”型开口是朝外还是朝内，其联系边5g既可以与电机筒壳1的壁面发生接触也可以不发生接触，其中以发生接触的情形为最佳。
本发明拉手卡件5采用勾接承力结构的优选例是：
拉手卡件5为独立件，并且在该拉手卡件5上设置有钩形结构5j勾接在电机筒壳1槽形孔洞4的内缘边4a上(如图17和图18所示)；需要说明的是，钩形结构5j既可以由外向里勾接在电机筒壳1的槽形孔洞4的内缘边4a上(如图17和图18所示)、也可以由里向外勾接在电机筒壳1的槽形孔洞4的内缘边4a上(图中未示出)，当钩形结构5j由外向里勾接在电机筒壳1的槽形孔洞4的内缘边4a上时，拉手卡件5的主体在电机筒壳1之外，反之当钩形结构5j由里向外勾接在电机筒壳1的槽形孔洞4的内缘边4a上时，拉手卡件5的主体在电机筒壳1里面；另外，让拉手卡件5与泵头主轴承座2之间保持有一定的轴向间隙有利于可靠紧固电机，显然当采用勾接结构时拉手卡件5的安装比较快捷。
本发明拉手卡件5采用卡接承力结构的若干优选例是：
拉手卡件5为独立件并卡接在电机筒壳的槽形孔洞4内(图中未示出)、或 者拉手卡件5与电机筒壳1为一体构件制作并且由冲制电机筒壳槽形孔洞4时冲制成弧形拱状(如图19和图20所示)；当拉手卡件5为独立件时，拉手卡件5卡接在电机筒壳1的槽形孔洞4的内缘边4a上，此时该拉手卡件5与槽形孔洞4之间既可以为松配合也可以为紧配合，其中以紧配合为较佳，因为这样在安装紧固螺栓3的过程中可以减少操作动作；当拉手卡件5与电机筒壳1为一体构件制作并且由冲制电机筒壳槽形孔洞4时冲制成弧形拱状时，弧形拱状的最佳布局是沿电机转子1b的轴向方向成形出孔洞或槽洞并在此基础上成形出第一螺纹孔5a(如图19和图20所示)或者成形出第一穿通孔5b(图中未示出)以便紧固螺栓3与之配合；需要说明的是，所述弧形拱状既可以向电机筒壳1的内部沉凹(图中未示出)也可以向电机筒壳1的外部隆起(如图19和图20所示)；需要指出的是，拉手卡件5采用卡接承力结构时，拉手卡件5上既可以开设第一螺纹孔5a(如图19和图20所示)也可以开设第一穿通孔5b(图中未示出)，另外拉手卡件5与泵头主轴承座2之间保持有一定的轴向间隙将有利于可靠紧固电机，显然当采用卡接结构时拉手卡件5的结构可以做得比较简单。
本发明拉手卡件5采用相连承力结构的若干优选例是：
拉手卡件5与电机筒壳1为一体构件，并且该拉手卡件5由冲制电机筒壳1的槽形孔洞4所形成的余料实行翻边弯折而成(如图21至图24所示)，此时可以在拉手卡件5上设置第一螺纹孔5a(如图21和图22所示)、也可以在拉手卡件5上开设第一穿通孔5b(如图23至图24所示)；显然，当拉手卡件5上开设第一穿通孔5b同时泵头主轴承座2上也开设第二穿通孔2a时可以配用螺帽6来紧固电机筒壳1(如图23和图24所示)，并进而可紧固电机。本发明在采用拉手卡件5与电机筒壳1为一体构件的时候，为了加强拉手卡件5的刚性，可 以在拉手卡件5上设置一定的加强翻边构造5k(如图21至图24所示)，其中加强翻边构造5k的最佳结构形式是沿着电机的轴向实施纵向分布并有一定的径向厚度，而且加强翻边构造5k最好与电机筒壳1的壁面发生接触。
本发明拉手卡件5采用开口槽状第一穿通孔5b的优选例是：
拉手卡件5上开设的第一穿通孔5b为开口槽状的结构形式(如图25和图26所示)，采用这种形式有利于快捷安装紧固螺栓3。
本发明泵头主轴承座2采用开口槽状第二穿通孔2a的优选例是：
泵头主轴承座2上开设的第二穿通孔2a为开口槽状的结构形式(图中未示出)，采用这种形式有利于快捷安装紧固螺栓3。
本发明相比现有技术具有的突出优点是：通过在靠近泵头主轴承座2设置拉手卡件5扣紧电机筒壳1的结构，使得紧固螺栓3的长度大大缩短，一方面大大增强了紧固螺栓3的扭转刚度，从而提高了压缩机电机与泵头的连接质量，另一方面节约了螺栓材料并可降低螺栓的装配难度，从而可以有效降低压缩机的生产成本。
上述实施例仅为本发明的较佳实施例之一，并非依此限制本发明的保护范围，故：凡依本发明的结构、形状、原理所做的各种等效变化，均应涵盖于本发明的保护范围之内。

Claims (15)

  1. 直联式空气压缩机电机紧固连接结构，包括电机筒壳、泵头主轴承座和紧固螺栓，其特征在于：在电机筒壳上成型有槽形孔洞，所述槽形孔洞位于电机筒壳靠近泵头主轴承座的一端，另外设置有与该槽形孔洞相呼应的拉手卡件，其中相互组配的拉手卡件和槽形孔洞之间存在相互承力的关系，电机筒壳与泵头主轴承座相互紧固连接的结构包含有以下三种情形之一：
    a)在拉手卡件上设置有第一螺纹孔、同时在泵头主轴承座上设置有与之呼应的第二穿通孔，所述紧固螺栓穿越第二穿通孔并与第一螺纹孔进行螺纹连接而将电机筒壳与泵头主轴承座相互拉紧；
    b)在拉手卡件上设置有第一穿通孔、同时在泵头主轴承座上设置有与之呼应的第二螺纹孔，所述紧固螺栓穿越第一穿通孔并与第二螺纹孔进行螺纹连接而将电机筒壳与泵头主轴承座相互拉紧；
    c)在拉手卡件上设置有第一穿通孔、同时在泵头主轴承座上设置有与之呼应的第二穿通孔，所述紧固螺栓穿越第二穿通孔及第一穿通孔并与螺帽进行螺纹连接而将电机筒壳与泵头主轴承座相互拉紧。
  2. 如权利要求1所述的直联式空气压缩机电机紧固连接结构，其特征在于：在所述的泵头主轴承座上设置有止口构造与电机筒壳作定位配合。
  3. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件为独立构件，并且该拉手卡件有一端搭靠在槽形孔洞的内缘边上、同时拉手卡件另有一端搭靠在泵头主轴承座上，拉手卡件上设置的第一螺纹孔或第一穿通孔布局在拉手卡件的中部区域。
  4. 如权利要求3所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件设置有定位折边，该定位折边与电机筒壳的壁面发生接触并受到 电机筒壳的限位、或者该定位折边与泵头主轴承座发生接触并受到泵头主轴承座的限位。
  5. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件为独立件并包含有“L”型构造，该拉手卡件的一边与电机筒壳的壁面存在有贴靠部位而成为扣紧边、拉手卡件的另一边穿越电机筒壳上的槽形孔洞而成为径向拉边，拉手卡件设置的第一螺纹孔或第一穿通孔布局在径向拉边上。
  6. 如权利要求5所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件的扣紧边设置有沉凹构造并借助该沉凹构造使该扣紧边与电机筒壳壁面的贴靠部位远离径向拉边一定距离。
  7. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件为独立件并包含有“U”型构造，该拉手卡件的中间部位为联系边、拉手卡件的两端相对于联系边朝同一侧向进行弯折并分别构成径向拉边和限位约束边，所述径向拉边及限位约束边均穿越电机筒壳上的槽形孔洞，拉手卡件设置的第一螺纹孔或第一穿通孔布局在径向拉边或/和限位约束边上。
  8. 如权利要求7所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件的径向拉边或/和限位约束边上设置有定位凸台构造。
  9. 如权利要求7所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件的径向拉边和限位约束边分别穿越电机筒壳上的两个相互独立的槽形孔洞。
  10. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件为独立件，并且该拉手卡件设置有钩形结构，所述钩 形结构勾接在电机筒壳槽形孔洞的内缘边上。
  11. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件为独立件并卡接在电机筒壳的槽形孔洞内、或者拉手卡件与电机筒壳为一体构件制作并且由冲制电机筒壳槽形孔洞时冲制成弧形拱状。
  12. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件与电机筒壳为一体构件，并且该拉手卡件由冲制电机筒壳槽形孔洞所形成的余料实行翻边弯折而成。
  13. 如权利要求12所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件有加强翻边构造。
  14. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述拉手卡件上开设的第一穿通孔为开口槽状的结构形式。
  15. 如权利要求1或者2所述的直联式空气压缩机电机紧固连接结构，其特征在于：所述泵头主轴承座上开设的第二穿通孔为开口槽状的结构形式。
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1045633A (zh) * 1989-03-16 1990-09-26 陈启星 隔离层密封式空气压缩机
JPH04112977A (ja) * 1990-09-03 1992-04-14 Mikuni Jukogyo Kk 住復動式真空ポンプ
CN104963822A (zh) * 2015-06-09 2015-10-07 安庆卡尔特压缩机有限公司 制冷剂用压缩机
CN105604918A (zh) * 2016-02-02 2016-05-25 浙江鸿友压缩机制造有限公司 直联式空气压缩机电机紧固连接结构
CN205370922U (zh) * 2016-02-02 2016-07-06 浙江鸿友压缩机制造有限公司 直联式空气压缩机电机紧固连接结构

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6530760B1 (en) * 2000-08-11 2003-03-11 Coleman Powermate, Inc. Air compressor
CN2482592Y (zh) * 2001-06-28 2002-03-20 大连通达空压机有限公司 全无油空压机
CN202926547U (zh) * 2012-11-22 2013-05-08 东莞瑞柯电子科技股份有限公司 一种空压机用直线式机芯
CN204627918U (zh) * 2015-05-13 2015-09-09 苏州欧圣电气工业有限公司 一种空压机把手的快速拆卸机构

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1045633A (zh) * 1989-03-16 1990-09-26 陈启星 隔离层密封式空气压缩机
JPH04112977A (ja) * 1990-09-03 1992-04-14 Mikuni Jukogyo Kk 住復動式真空ポンプ
CN104963822A (zh) * 2015-06-09 2015-10-07 安庆卡尔特压缩机有限公司 制冷剂用压缩机
CN105604918A (zh) * 2016-02-02 2016-05-25 浙江鸿友压缩机制造有限公司 直联式空气压缩机电机紧固连接结构
CN205370922U (zh) * 2016-02-02 2016-07-06 浙江鸿友压缩机制造有限公司 直联式空气压缩机电机紧固连接结构

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