CN107143484B - Piston air compressor and automobile-used air compressor - Google Patents
Piston air compressor and automobile-used air compressor Download PDFInfo
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- CN107143484B CN107143484B CN201710312205.7A CN201710312205A CN107143484B CN 107143484 B CN107143484 B CN 107143484B CN 201710312205 A CN201710312205 A CN 201710312205A CN 107143484 B CN107143484 B CN 107143484B
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- crank
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H21/00—Gearings comprising primarily only links or levers, with or without slides
- F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
- F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
- F16H21/18—Crank gearings; Eccentric gearings
- F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
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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
- F04B39/0027—Pulsation and noise damping means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/06—Crankshafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/06—Crankshafts
- F16C3/10—Crankshafts assembled of several parts, e.g. by welding by crimping
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
- F16C3/18—Eccentric-shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H21/00—Gearings comprising primarily only links or levers, with or without slides
- F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
- F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
- F16H21/18—Crank gearings; Eccentric gearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2240/00—Components
- F04C2240/60—Shafts
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
A piston type air compressor comprises a machine body, a first rotary reciprocating motion conversion device, a second rotary reciprocating motion conversion device and a driving device, wherein the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device are arranged in the machine body; each rotary reciprocating motion conversion device comprises a combined crankshaft, an eccentric shaft and two double-acting reciprocating motion pistons; the combined crankshaft comprises main journals, two crank arms and a crank pin, wherein the main journals are coaxially arranged at two ends of the combined crankshaft; the eccentric shaft comprises a hollow shaft section and two eccentric cylinders which are arranged on the hollow shaft section and have 180-degree phase positions; the hollow shaft section of the eccentric shaft is rotatably sleeved on a crank pin of the combined crankshaft, a piston seat of the double-acting piston is rotatably sleeved on an eccentric cylinder of the eccentric shaft, and the reciprocating directions of the double-acting pistons arranged outside the two eccentric cylinders are arranged at 90 degrees.
Description
The present application claims priority of chinese patent application with application number 201710236724.X entitled "piston air compressor, motion conversion device, combined crankshaft, eccentric shaft and vehicular air compressor" filed on 12.4.2017, which is incorporated herein by reference in its entirety.
Technical Field
The invention relates to the technical field of air compressors. In particular to a piston type air compressor. The application still relates to an automobile-used air compressor machine.
Background
At present, most of mainstream air compressors for vehicle braking adopt a compressor assembly formed by two V-shaped double-cylinder air compressors coaxially driven by a motor. For each V-shaped air compressor, a single-crank crankshaft is adopted, more than two pistons forming an angle of 90 degrees with each other are arranged on a crank pin of the crankshaft, a connecting structure of the pistons and the crank pin is a crank connecting rod structure, and no balance weight is arranged on a machine. The air compressor with the structure has the advantages of simple structure and easy maintenance, but the flow is small, the vibration is large, and the requirements of increasing the size and comfort of vehicles are difficult to meet.
Disclosure of Invention
The invention provides a piston type air compressor, which aims to solve the problems of the piston type air compressor. The invention also provides a rotary reciprocating motion conversion device, a combined crankshaft, an eccentric shaft and a vehicle air compressor.
The application provides a piston type air compressor, which comprises a machine body, a first rotary reciprocating motion conversion device, a second rotary reciprocating motion conversion device and a driving device, wherein the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device are arranged in the machine body;
each rotary reciprocating motion conversion device comprises a combined crankshaft, an eccentric shaft and two double-acting reciprocating motion pistons;
the combined crankshaft comprises main journals, two crank arms and a crank pin, wherein the main journals are coaxially arranged at two ends of the combined crankshaft, the two crank arms are arranged at opposite ends of the two main journals, the crank pin is arranged between the two crank arms, at least one crank arm at one end of the crank pin is of a detachable structure, and the crank pin and the crank arm at the other end of the crank pin are connected into a whole through a connecting piece;
the eccentric shaft comprises a hollow shaft section and two eccentric cylinders arranged on the hollow shaft section, the hollow shaft section penetrates through the two eccentric cylinders, the phases of the two eccentric cylinders are arranged in 180 degrees, and the two eccentric cylinders are symmetrically arranged on two sides of the axis of the hollow shaft section;
the double-acting reciprocating piston comprises pistons positioned on two sides and a piston seat connected with the two pistons, and an eccentric cylinder containing hole is formed in the piston seat;
during assembly, the hollow shaft section of the eccentric shaft is rotatably sleeved on the crank pin of the combined crankshaft, the piston seat of each double-acting piston is rotatably sleeved on an eccentric cylinder of the eccentric shaft, the reciprocating directions of the double-acting pistons arranged outside the two eccentric cylinders are arranged in 90 degrees, the assembled first rotating reciprocating motion conversion device and the assembled second rotating reciprocating motion conversion device are arranged on the machine body, and the crankshafts of the two rotating reciprocating motion conversion devices are connected with the driving shaft of the driving device.
Optionally, the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device are symmetrically arranged on the machine body; and the crankshafts of the two rotary reciprocating motion conversion devices are coaxially connected with the driving shafts of the driving devices.
Optionally, oilless bearings are used for connecting the piston and the eccentric cylinder and between the hollow shaft section and the crankshaft.
Optionally, the combined crankshaft comprises
The crank arm assembly comprises a main end and an auxiliary end, wherein the main end comprises a first main journal, a first crank arm integrally arranged with the first main journal, and a first crank pin extending outwards from one end, far away from the first main journal, of the first crank arm; the first crank pin is of a hollow structure, the hollow structure extends to the free end of the first main journal along the axis of the first crank pin, and the free end of the first crank pin is a conical end;
the auxiliary end comprises a second main journal, a second crank arm integrally arranged with the second main journal, and a second crank pin extending outwards from one end, far away from the second main journal, of the second crank arm; the free end of the second crank pin is provided with a taper hole matched with the taper end, and the bottom of the taper hole is also provided with a threaded hole;
during combination, after the taper end of the first crank pin of the main end is matched with the taper hole of the second crank pin of the auxiliary end, the bolt penetrates through the main end and rotates into the threaded hole of the auxiliary end, and the main end and the auxiliary end are combined into a whole.
Optionally, a positioning structure is further disposed on the portion where the taper end and the taper hole are matched.
Optionally, the positioning structure is two pairs of half holes and two positioning pins arranged at corresponding positions of the conical end and the conical hole; after combination, the two half-hole holes at corresponding positions are aligned to form a complete positioning hole, and the positioning pin is arranged in the positioning hole.
Optionally, a balance weight is further disposed on two crank arms of the combined crankshaft.
Optionally, opposite ends of two crank arms of the combined crankshaft are respectively provided with a circular groove along a crank pin, and two ends of the hollow eccentric shaft are supported on side walls of the circular grooves through bearings.
Alternatively, the piston is directly connected with the eccentric cylinder of the eccentric shaft through a rolling bearing.
Optionally, the eccentric cylinder is integrally formed with the hollow shaft section, or
The eccentric cylinder and the hollow shaft section are of a split structure fixedly connected into a whole.
Optionally, a rolling bearing is sleeved on the periphery of the eccentric cylinder, and the periphery of the eccentric cylinder forms an inner ring of the rolling bearing.
Optionally, the reciprocating direction of the two reciprocating pistons far away from the driving device is the same, and the reciprocating direction of the two reciprocating pistons close to the driving device is the same.
Optionally, the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device are arranged to meet the synchronous motion of the reciprocating pistons with the same reciprocating direction.
In addition, this application still provides an automobile-used air compressor machine, wherein, this air compressor machine adopts aforementioned arbitrary piston air compressor.
Compared with the prior art, one aspect of the application has the following advantages: compared with the existing piston type air compressor with two 2V structures, the piston type air compressor with the structure has the advantage that the displacement is doubled without increasing the volume of the compressor body. In addition, this application structure balance performance is good, and the vibration is little. Can meet the requirements of large-scale and comfort of the vehicle adopting the air compressor.
Drawings
Fig. 1 and 2 are a schematic structural view and a sectional view, respectively, of a rotary-to-reciprocating motion converting apparatus of a piston type air compressor according to a first embodiment of the present application;
FIG. 3, FIG. 4 and FIG. 5 are the first, the second and the first cross-sectional views of the eccentric shaft of the first embodiment of the present application
FIGS. 6 and 7 are schematic views showing the main end structures of the compound crankshaft according to the first embodiment of the present application;
FIGS. 8 and 9 are schematic views showing the structure of the secondary end of the compound crankshaft in the first embodiment of the present application;
FIGS. 10, 11 and 12 are schematic structural views of a double acting reciprocating piston according to an embodiment of the present application;
fig. 13 shows a schematic structural view of the piston air compressor of the present embodiment.
Detailed Description
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. This invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein, but rather construed as limited to the embodiments set forth herein.
In the following embodiments of the present application, a piston air compressor is provided. The piston type air compressor comprises a machine body, a driving device, a first rotary reciprocating motion conversion device and a second rotary reciprocating motion conversion device. The machine body is matched with the driving device, the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device, and the structure of the existing piston type air compressor machine body can be adopted. The drive means may be an electric motor or an internal combustion engine or other power means. The output power is determined according to the displacement and the rotating speed of the piston type air compressor. The piston type air compressor of the embodiment of the application also comprises two rotary reciprocating motion conversion devices with the same structure, wherein each device comprises a combined crankshaft, an eccentric shaft and two double-acting reciprocating motion pistons;
the combined crankshaft comprises main journals, two crank arms and a crank pin, wherein the main journals are coaxially arranged at two ends of the combined crankshaft, the two crank arms are arranged at opposite ends of the two main journals, the crank pin is arranged between the two crank arms, at least one crank arm at one end of the crank pin is of a detachable structure, and the crank pin and the crank arm at the other end of the crank pin are connected into a whole through a connecting piece;
the eccentric shaft comprises a hollow shaft section and two eccentric cylinders arranged on the hollow shaft section, the hollow shaft section penetrates through the two eccentric cylinders, the phases of the two eccentric cylinders are arranged in 180 degrees, and the two eccentric cylinders are symmetrically arranged on two sides of the axis of the hollow shaft section;
the double-acting reciprocating piston comprises pistons positioned on two sides and a piston seat connected with the two pistons, and an eccentric cylinder containing hole is formed in the piston seat;
during assembly, the hollow shaft section of the eccentric shaft is rotatably sleeved on a crank pin of the combined crankshaft, the piston seat of each double-acting piston is rotatably sleeved on an eccentric cylinder of the eccentric shaft, and the reciprocating motion directions of the double-acting pistons arranged outside the two eccentric cylinders are arranged at 90 degrees;
and the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device are arranged on the machine body after being assembled, and crankshafts of the two rotary reciprocating motion conversion devices are connected with a driving shaft of the driving device.
The two rotary reciprocating motion conversion devices are driven to move by the driving shaft of the driving device, so that the conversion from rotary motion to reciprocating motion is realized, and a reciprocating piston moves in a cylinder to compress gas.
The piston air compressor of the present application will be described in detail with reference to specific embodiments.
The present embodiment is a piston type air compressor of 8-cylinder double cross type structure (or called double X type structure). Fig. 13 shows a schematic structural diagram of the piston type air compressor of the present embodiment, and in the present embodiment, the piston type air compressor of the present embodiment is mainly described in conjunction with the arrangement form thereof, and the machine body, the driving device and the accessories of the compressor are not described too much, and the related matters can refer to the existing piston type air compressor.
Referring to fig. 13, the 8-cylinder dual-cross structure of the present embodiment includes eight compression cylinders 200, which are respectively disposed at two sides of the compressor and four cylinders at one side. Four cylinders on one side are arranged in a cross shape, and a driving device is arranged in the middle, wherein the driving device is a driving motor 100 in the embodiment. The entire machine is set on the base 300.
The piston air compressor of the present embodiment includes, in addition to the machine body and the driving device, two rotary-to-reciprocating motion conversion devices, which are respectively referred to as a first rotary-to-reciprocating motion conversion device and a second rotary-to-reciprocating motion conversion device. In this embodiment, the two rotary reciprocating motion conversion devices may have the same structure, and are symmetrically disposed on opposite sides of the machine body and connected to each other through a driving shaft of the driving device. Of course, the two-side rotary-reciprocating motion converting mechanism may be disposed asymmetrically. One of the rotary-to-reciprocating motion converting apparatuses will be described below. Fig. 1 and 2 are a schematic structural view and a sectional view of a rotary-to-reciprocating motion converting apparatus of a piston type air compressor according to an embodiment of the present application, respectively.
Referring to fig. 1 and 2, the rotary-to-reciprocating motion converting apparatus in the present embodiment includes a combined crankshaft 20, an eccentric shaft 30, and two double-acting pistons 10. The two double-acting pistons are arranged at 90 degrees in the reciprocating direction and are connected 20 with the combined crankshaft through eccentric shafts 30. The mechanism of the compound crankshaft 20, the off-axis 30 and the double-acting piston 10, and the direct interconnection of the aforementioned components, respectively, are described below.
Referring further to fig. 2, the combined crankshaft of the present embodiment includes a main end 20a and a secondary end 20 b. Fig. 6 and 7 show schematic structural views of the main terminal of the present embodiment. The main end 20a comprises a first main journal 2-1, a crank arm 2-2 integrally arranged with the first main journal 2-1, and a first crank pin 2-3 extending outwards from one end of the first crank arm 2-2 far away from the first main journal 2-1, wherein the first crank pin 2-3 is not coaxial with the first main journal 2-1, and the axial distance between the first crank pin 2-3 and the first main journal 2-1 is e. The free end of the first crank pin 2-3 (i.e. the end away from the first main journal 2-1) is a tapered end 2-5. The first crank pin 2-3 is hollow, that is, the first crank pin 2-3 is provided with a through hole 2-6 along the axial direction, and the through hole 2-6 extends to the free end of the first main journal 2-1 along the first crank pin 2-3 (as shown in fig. 7). The through holes 2-6 are used for passing through bolts for fixing the main end and the auxiliary end. For the convenience of bolt fixing, a bolt countersunk hole 2-4a (shown in fig. 7) is further formed at the free end side of the first main journal 2-1, and the aperture of the countersunk hole 2-4a is larger than that of the through hole 2-6, so as to accommodate the bolt countersunk head and facilitate bolt fixing.
Referring to fig. 8 and 9, the secondary end includes a second main journal 3-1, a second crank arm 3-2 integrally disposed with the second main journal 3-1, and a second crank pin 3-3 extending outward from an end of the second crank arm 3-2 away from the second main journal 3-1. The second crank pin 3-3 and the second main journal 3-1 are not coaxial, and the distance between the axes is e. The free end of the second crank pin 3-3 (i.e. the end far away from the second main journal 3-1) is provided with a conical hole 3-5 with which the conical end 2-5 is matched. And a positioning structure can be arranged at the matching part of the taper hole 3-5 and the taper end. For example, two pairs of half holes are arranged at the corresponding positions of the conical end 2-5 and the conical hole 3-5 and are matched with the two half holes through two positioning pins; after combination, two half holes at corresponding positions are aligned to form a complete positioning hole, and the positioning pin is arranged in the positioning hole to complete positioning after the main end and the auxiliary end are assembled. In addition, threaded holes 3-7 (shown in fig. 9) are formed in the bottoms of the tapered holes 3-5, and the threaded holes 3-7 are matched with the fixing bolts and used for fixing the main end and the auxiliary end after the main end and the auxiliary end are assembled.
When the crank pin and the crank pin are combined, the conical end 2-5 of the first crank pin 2-3 of the main end 20a is inserted into the conical hole 3-5 of the second crank pin 3-3 of the auxiliary end 20b, and the two are matched, and the arrangement of the conical hole and the conical end ensures that the first crank pin 2-3 and the second crank pin 3-3 have a common axis after being matched. Further, the positions of the primary end 20a and the secondary end 20b in the circumferential direction are adjusted so that the first main journal 2-1 and the second main journal 3-1 are coaxial, and if necessary, it is also possible to arrange to perform the coaxial arrangement by a positioning structure. A fixing bolt (e.g., fixing bolt 80 in fig. 2) is passed through the through hole 2-6 from the side of the countersunk hole 2-4a, screwed into the threaded hole 3-7, and tightened.
In addition, the first main journal 2-1 and the first crank arm 2-2, and the second main journal 3-1 and the second crank arm 3-2 may not be an integral structure, but may be a split structure, and are fixedly connected into a whole through a connecting structure or a connecting piece.
In addition, in order to ensure the balance of the whole compressor, a balance arrangement can be arranged on the crank arms of the combined crank shaft, such as a balance weight 2-4 arranged on the first crank arm 2-2 and a balance weight 3-4 arranged on the second crank arm 3-2.
In addition, the combined crankshaft can also have other combination modes, for example, the crank pin is a whole, and the crank pin and any crank arm are of a combined structure and are fixedly connected into a whole through bolts. Or the crank pin and the crank arms at the two ends are of detachable structures, and the description is omitted.
Please refer to fig. 3, fig. 4 and fig. 5, which are respectively a first, a second and a first cross-sectional view of a structure of an eccentric shaft according to an embodiment of the present application. The eccentric shaft of the present embodiment comprises a hollow shaft section 4-1 and two eccentric cylinders 4-2a and 4-2b arranged on said hollow shaft section. The hollow shaft section 4-1 is provided with a hollow through hole 4-1a (see fig. 5) along the axial direction, and the axial length of the hollow shaft section 4-1 is not less than the axial length of the crank pin of the combined crankshaft 20 (the first crank pin and the second crank pin constitute a complete crank pin). The radial dimension of the hollow through hole 4-1a is larger than that of the crank pin of the aforementioned compound crankshaft 20. The radial and axial dimensions of the two eccentric cylinders are the same, and the phase positions are arranged at 180 degrees. The axes of the two are symmetrically arranged at the two sides of the central axis of the hollow shaft section 4-1, and the distances from the central axis of the hollow shaft section 4-1 are both e. The two eccentric cylinders 4-2a and 4-2b and the hollow shaft section 4-1 can be integrally formed or can be in a combined structure. When the structure is a combined structure, eccentric holes are arranged on the two eccentric cylindrical drawings 4-2a and 4-2b, and the hollow shaft section 4-1 penetrates through the eccentric holes and is fixed with the eccentric cylindrical drawings into a whole.
Weight-reducing structures may also be provided on the two eccentric cylinders 4-2a and 4-2b, for example weight-reducing grooves 4-6 may also be provided on the respective opposite end face sides.
In addition, a rolling bearing can be sleeved on the periphery of the eccentric cylinder, in a specific example, the periphery of the eccentric cylinder forms a bearing inner ring of the rolling bearing, the roller pins or the balls are directly contacted with the periphery of the eccentric cylinder, and the bearing outer ring 4-5 is sleeved outside the roller pins or the balls. The specific structure is shown in fig. 5.
The hollow shaft section 4-1 of the eccentric shaft 30 is rotatably fitted over the crank pin of the assembled crankshaft 20. In this embodiment, the opposite ends of the two crank arms of the assembled crankshaft 20 are each provided with a circular groove along the crank pin, and the crank arm 2-2 at the main end 20a of fig. 6 is provided with a supporting circular groove 2-2a, and the crank arm 3-2 at the auxiliary end 20b of fig. 9 is provided with a supporting circular groove 3-2 a. The crank arms pass through the hollow through holes 4-1a of the hollow shaft section 4-1 of the eccentric shaft 30 and are supported in the supporting circular grooves 2-2a and 3-2a by rolling bearings 4-7 (shown in fig. 4 and 5) provided on the outer sides of both ends of the hollow shaft section 4-1. The rolling bearings 4-7 can be arranged in the same way as the outer bearings of the eccentric cylindrical figure, i.e. the rolling elements and the outer bearing rings are arranged only on the outside of the hollow shaft section. The rolling bearing arranged on the eccentric shaft can meet the requirement that lubricating oil is not needed for lubricating relative motion between the eccentric shaft and the combined crankshaft and between the eccentric shaft and a piston. The bearing is filled with lubricating grease to ensure long-time relative movement, so that the air compressor with the structure can be called as an oilless air compressor in a certain sense. Because no lubricating oil is needed, the maintenance and repair cost is greatly reduced, and the effective operation time is prolonged.
The eccentric shaft and the combined crankshaft may furthermore have other ways of achieving a rotatable connection, for example by providing a rolling bearing between the hollow bearing of the eccentric shaft and the crank pin of the combined crankshaft. And will not be discussed further herein.
In addition, it should be noted that the rotatable connection between the eccentric shaft and the combined crankshaft does not necessarily need to adopt the rolling bearing, but may also be a sliding bearing or other mode of a die-reducing sleeve, or a wear-reducing layer is arranged on a joint surface which moves relative to the combined crankshaft. The outside of the eccentric cylinder may also be provided with a sliding bearing or other mode of die-reducing sleeve, or a wear-reducing layer on the surface of relative motion with the piston, etc., and will not be discussed herein.
In this embodiment, the combination crank pin passes through the structure of the hollow shaft section of eccentric shaft for the crank pin has the effect of synchronizing shaft, and need not to set up the synchronizing shaft alone again. The air compressor machine of make full use of design space for the device of this application embodiment has less volume.
Referring to fig. 10, fig. 11 and fig. 12, which are schematic structural views of a double-acting reciprocating piston according to an embodiment of the present invention, in this embodiment, the double-acting reciprocating piston includes piston heads 5a and 5b, a piston seat is a split structure, and includes a first portion 5-2a and a second portion 5-5b, which are fixed together by a connecting structure disposed on an outer edge, such as the connecting hole 5-5 in fig. 12. The middle of the piston seat is provided with an eccentric cylinder containing hole 5-3. The small head part of the piston seat is provided with a pin hole 5-4, and the piston seat is connected with the piston head through the pin hole 5-4 and a piston pin.
In this embodiment, each rotary-to-reciprocating motion conversion device includes two double-acting reciprocating pistons. After being assembled with the combined crankshaft and the eccentric shaft, each double-acting reciprocating piston corresponds to an eccentric cylinder which can be rotatably arranged in a containing hole of the double-acting reciprocating piston. The reciprocating directions of the double-acting pistons arranged outside the two eccentric cylinders are 90 degrees.
The assembled first rotary reciprocating motion conversion device and the assembled second rotary reciprocating motion conversion device are both arranged on the machine body, crankshafts of the two rotary reciprocating motion conversion devices are both connected with a driving shaft of the driving device, and the assembled structure is shown in fig. 13.
In a specific example, the cylinders of the rotary reciprocating motion converting device at both sides of the driving device 10 are arranged correspondingly, the reciprocating directions of the two reciprocating pistons at the outer side of the whole machine (both sides far away from the driving device) are the same, the reciprocating directions of the two reciprocating pistons near the driving device are the same, and the two pistons with the same moving direction reach the top dead center in the same direction at the same time. I.e. the reciprocating pistons with the same reciprocating direction move synchronously. The arrangement structure can further reduce the moment of the whole machine, so that the balance performance of the machine is greatly improved.
The structure balance performance of the air compressor arrangement mode of the embodiment of the application is greatly enhanced, so that the whole machine has excellent balance performance. The two rotary reciprocating motion conversion structures are the same, can be symmetrically arranged on two sides of the machine body and are connected through a motor driving shaft, for example, can be coaxially connected.
Furthermore, compared with the existing two piston type air compressors with 2V structures, the piston type air compressor with the structure also doubles the displacement under the condition that the volume of the machine body is not increased.
In addition, the present application also provides a rotary reciprocating motion conversion device, and the structure of the rotary reciprocating motion conversion device can adopt the rotary reciprocating motion conversion device described in the above embodiment. And will not be discussed further herein.
In addition, the application also provides a combined crankshaft, and the structure of the combined crankshaft can adopt the combined crankshaft in the embodiment. And will not be discussed further herein.
In addition, the application also provides an eccentric shaft, and the structure of the eccentric shaft can adopt the eccentric shaft in the embodiment. And will not be discussed further herein.
The application still provides an automobile-used air compressor machine, for locomotive or car braking provide power, this automobile-used air compressor machine adopts above-mentioned arbitrary embodiment piston air compressor machine.
Although the present invention has been described with reference to the preferred embodiments, it is not intended to be limited thereto, and variations and modifications may be made by those skilled in the art without departing from the spirit and scope of the present invention.
Claims (14)
1. A piston type air compressor is characterized by comprising a machine body, a first rotary reciprocating motion conversion device, a second rotary reciprocating motion conversion device and a driving device, wherein the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device are arranged in the machine body;
each rotary reciprocating motion conversion device comprises a combined crankshaft, an eccentric shaft and two double-acting reciprocating motion pistons;
the combined crankshaft comprises main journals, two crank arms and a crank pin, wherein the main journals are coaxially arranged at two ends of the combined crankshaft, the two crank arms are arranged at opposite ends of the two main journals, the crank pin is arranged between the two crank arms, at least one crank arm at one end of the crank pin is of a detachable structure, and the crank pin and the crank arm at the other end of the crank pin are connected into a whole through a connecting piece;
the eccentric shaft comprises a hollow shaft section and two eccentric cylinders arranged on the hollow shaft section, the hollow shaft section penetrates through the two eccentric cylinders, the phases of the two eccentric cylinders are arranged in 180 degrees, and the two eccentric cylinders are symmetrically arranged on two sides of the axis of the hollow shaft section;
the double-acting reciprocating piston comprises pistons positioned on two sides and a piston seat connected with the two pistons, and an eccentric cylinder containing hole is formed in the piston seat;
during assembly, the hollow shaft section of the eccentric shaft is rotatably sleeved on the crank pin of the combined crankshaft, the piston seat of each double-acting piston is rotatably sleeved on an eccentric cylinder of the eccentric shaft, the reciprocating directions of the double-acting pistons arranged outside the two eccentric cylinders are arranged at 90 degrees,
and the first rotary reciprocating motion conversion device and the second rotary reciprocating motion conversion device are arranged on the machine body after being assembled, and crankshafts of the two rotary reciprocating motion conversion devices are connected with a driving shaft of the driving device.
2. The piston air compressor as claimed in claim 1, wherein said first and second rotary to and fro motion converting means are symmetrically disposed on said housing; and the crankshafts of the two rotary reciprocating motion conversion devices are coaxially connected with the driving shaft of the driving device.
3. The piston air compressor as claimed in claim 1, wherein oilless bearings are used to connect the piston to the eccentric cylinder and the hollow shaft section to the crankshaft.
4. The piston air compressor as claimed in claim 1, wherein said compound crankshaft comprises:
the crank arm assembly comprises a main end and an auxiliary end, wherein the main end comprises a first main journal, a first crank arm integrally arranged with the first main journal, and a first crank pin extending outwards from one end, far away from the first main journal, of the first crank arm; the first crank pin is of a hollow structure, the hollow structure extends to the free end of the first main journal along the axis of the first crank pin, and the free end of the first crank pin is a conical end;
the auxiliary end comprises a second main journal, a second crank arm integrally arranged with the second main journal, and a second crank pin extending outwards from one end, far away from the second main journal, of the second crank arm; the free end of the second crank pin is provided with a taper hole matched with the taper end, when the bottom of the taper hole is further provided with a threaded hole combination, the taper end of the first crank pin of the main end is matched with the taper hole of the second crank pin of the auxiliary end, the main end is penetrated through the bolt and screwed into the threaded hole of the auxiliary end, and the main end and the auxiliary end are combined into a whole.
5. The piston type air compressor as claimed in claim 4, wherein a positioning structure is further provided at the portion where the taper end and the taper hole are engaged.
6. The piston type air compressor as claimed in claim 5, wherein the positioning structure is two pairs of half holes and two positioning pins disposed at corresponding positions of the taper end and the taper hole; after combination, the two half-hole holes at corresponding positions are aligned to form a complete positioning hole, and the positioning pin is arranged in the positioning hole.
7. The piston air compressor as claimed in claim 1, further comprising a balance weight on both crank arms of said compound crankshaft.
8. The piston type air compressor as claimed in any one of claims 1 to 7, wherein circular grooves are opened along a crank pin at opposite ends of both crank arms of said assembled crank shaft, and both ends of said hollow eccentric shaft are supported by side walls of said circular grooves through bearings.
9. The piston air compressor as claimed in any one of claims 1 to 7, characterized in that the piston is connected with the eccentric cylinder of the eccentric shaft by means of a rolling bearing.
10. The piston air compressor as claimed in claim 1, characterized in that the eccentric cylinder is integrally formed with the hollow shaft section, or
The eccentric cylinder and the hollow shaft section are of a split structure fixedly connected into a whole.
11. The piston air compressor as claimed in claim 1, wherein a rolling bearing is sleeved on an outer circumference of the eccentric cylinder, and the outer circumference of the eccentric cylinder constitutes an inner ring of the rolling bearing.
12. The piston air compressor as claimed in claim 1, wherein the reciprocating direction of the two reciprocating pistons located away from the drive means is the same and the reciprocating direction of the two reciprocating pistons located close to the drive means is the same.
13. The piston air compressor as claimed in claim 12, wherein said first and second rotary to and fro motion converting means are arranged to provide synchronous motion of the reciprocating pistons in the same direction of reciprocation.
14. An air compressor for a vehicle, characterized in that the air compressor employs a piston-type air compressor according to any one of claims 1 to 13.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710236724 | 2017-04-12 | ||
| CN201710236724X | 2017-04-12 |
Publications (2)
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| CN107143484A CN107143484A (en) | 2017-09-08 |
| CN107143484B true CN107143484B (en) | 2020-01-24 |
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|---|---|---|---|
| CN201720493714.XU Withdrawn - After Issue CN207620993U (en) | 2017-04-12 | 2017-05-05 | A kind of piston type air compressor and vehicle air compressor |
| CN201720493310.0U Active CN207297610U (en) | 2017-04-12 | 2017-05-05 | Vuilt-up crankshaft, include no connecting rod rotary reciprocating motion transformational structure equipment |
| CN201710312833.5A Pending CN106949214A (en) | 2017-04-12 | 2017-05-05 | Rotary reciprocating motion conversion equipment and the equipment using the device |
| CN201720493316.8U Active CN207278692U (en) | 2017-04-12 | 2017-05-05 | Eccentric shaft, include no connecting rod rotary reciprocating motion transformational structure equipment |
| CN201720493773.7U Withdrawn - After Issue CN207761902U (en) | 2017-04-12 | 2017-05-05 | A kind of piston type air compressor and vehicle air compressor |
| CN201710312205.7A Active CN107143484B (en) | 2017-04-12 | 2017-05-05 | Piston air compressor and automobile-used air compressor |
| CN201710312751.0A Active CN107143485B (en) | 2017-04-12 | 2017-05-05 | A kind of piston type air compressor and vehicle air compressor |
| CN201710312859.XA Pending CN106979218A (en) | 2017-04-12 | 2017-05-05 | A kind of eccentric shaft |
| CN201720492843.7U Active CN207316001U (en) | 2017-04-12 | 2017-05-05 | Rotary reciprocating motion conversion equipment and the equipment using the device |
Family Applications Before (5)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201720493714.XU Withdrawn - After Issue CN207620993U (en) | 2017-04-12 | 2017-05-05 | A kind of piston type air compressor and vehicle air compressor |
| CN201720493310.0U Active CN207297610U (en) | 2017-04-12 | 2017-05-05 | Vuilt-up crankshaft, include no connecting rod rotary reciprocating motion transformational structure equipment |
| CN201710312833.5A Pending CN106949214A (en) | 2017-04-12 | 2017-05-05 | Rotary reciprocating motion conversion equipment and the equipment using the device |
| CN201720493316.8U Active CN207278692U (en) | 2017-04-12 | 2017-05-05 | Eccentric shaft, include no connecting rod rotary reciprocating motion transformational structure equipment |
| CN201720493773.7U Withdrawn - After Issue CN207761902U (en) | 2017-04-12 | 2017-05-05 | A kind of piston type air compressor and vehicle air compressor |
Family Applications After (3)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710312751.0A Active CN107143485B (en) | 2017-04-12 | 2017-05-05 | A kind of piston type air compressor and vehicle air compressor |
| CN201710312859.XA Pending CN106979218A (en) | 2017-04-12 | 2017-05-05 | A kind of eccentric shaft |
| CN201720492843.7U Active CN207316001U (en) | 2017-04-12 | 2017-05-05 | Rotary reciprocating motion conversion equipment and the equipment using the device |
Country Status (1)
| Country | Link |
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| CN (9) | CN207620993U (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN207620993U (en) * | 2017-04-12 | 2018-07-17 | 中清能（北京）科技有限公司 | A kind of piston type air compressor and vehicle air compressor |
| JP6281853B1 (en) * | 2017-10-03 | 2018-02-21 | 有限会社ケイ・アールアンドデイ | Rotary cylinder device |
| CN108523778A (en) * | 2018-06-13 | 2018-09-14 | 山西嘉世达机器人技术有限公司 | Clean robot |
| CN108433633A (en) * | 2018-06-13 | 2018-08-24 | 山西嘉世达机器人技术有限公司 | Dustbin and clean robot with it |
| DE102018125866B3 (en) * | 2018-10-18 | 2019-06-27 | Schaeffler Technologies AG & Co. KG | unbalanced shaft |
| CN109537346B (en) * | 2019-01-08 | 2024-06-18 | 山东力脉智能科技股份有限公司 | Eccentric swinging shaft, manufacturing method thereof and dustpan sieve |
| CN110056494A (en) * | 2019-05-20 | 2019-07-26 | 浙江万安其弗汽车零部件有限公司 | A kind of automobile-used oil-free air compressor |
| CN110295995B (en) * | 2019-07-17 | 2022-02-11 | 李洋涛 | Structure capable of realizing full balance and multi-cylinder combined piston engine |
| CN110863968B (en) * | 2019-12-12 | 2024-05-03 | 浙江洛森压缩机股份有限公司 | Double-pump-head air compressor |
| CN113565730A (en) * | 2021-08-26 | 2021-10-29 | 瑞立集团瑞安汽车零部件有限公司 | Novel reciprocating positive displacement air compressor |
| US11536353B1 (en) * | 2021-12-02 | 2022-12-27 | Sencera Energy, Inc. | Apparatus and method for converting between linear and rotary motion and systems involving the same |
| CN114623064A (en) * | 2022-03-09 | 2022-06-14 | 王汝君 | Parallel multi-cylinder star-like piston compressor |
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Also Published As
| Publication number | Publication date |
|---|---|
| CN106979218A (en) | 2017-07-25 |
| CN207620993U (en) | 2018-07-17 |
| CN107143485A (en) | 2017-09-08 |
| CN107143484A (en) | 2017-09-08 |
| CN207761902U (en) | 2018-08-24 |
| CN207278692U (en) | 2018-04-27 |
| CN106949214A (en) | 2017-07-14 |
| CN107143485B (en) | 2019-10-18 |
| CN207297610U (en) | 2018-05-01 |
| CN207316001U (en) | 2018-05-04 |
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