CN205744457U - Oil supply device for compressor and compressor - Google Patents

Abstract

The utility model provides an oil supply unit for compressor, it includes: a pump driven by a rotating shaft of the compressor, the pump including an oil inlet hole and an oil discharge hole, the oil inlet hole being fluidly connected to an oil sump of the compressor, wherein a lubricating oil is stored in the oil sump; an oil supply passage including a first end fluidly connected to the oil drain hole; and a valve member provided in the oil supply passage and configured to perform an opening degree changing operation in response to a pressure difference across the valve member. The utility model also provides a compressor including this oil supply unit.

Description

Fueller and compressor for compressor

Technical field

This utility model relates to a kind of fueller for compressor and one includes this fuel feeding The compressor of device.

Background technology

The content of this part provide only the background information relevant to this utility model, and it may be not Constitute prior art.

It is known that need between all parts in compressor to supply lubricating oil, with play heat radiation, Seal, reduce the effects such as abrasion.In the prior art, generally by means of cold-producing medium, lubricating oil is taken Band is to parts to be lubricated.But, for variable speed compressor is such as frequency-changeable compressor, cold-producing medium The amount of entrained lubricating oil often with system frequency (the such as drive mechanism or rotary shaft of compressor Rotating speed) relevant.In the case of compressor assembly frequency or rotating speed are relatively low, lubricating oil quantity delivered May be too low so that the lubricant effect of all parts in compressor declines, and then reduce compressor Performance.In the case of compressor assembly frequency or rotating speed are higher, lubricating oil quantity delivered may again can Too high, thus cause the heat exchange efficiency being positioned at the heat exchanger in compressor downstream to decline, but also meeting Cause lubricant in compressor the most exhausted, make compressor impaired.

Utility model content

As it has been described above, need exist for can solve the problem that confession when (variable speed) compressor slow-speed of revolution runs The effective technology means of shortage of oil.

One purpose of one or more embodiment of the present utility model is to provide one and can carry The fueller of the lubricant effect of high compressor.

The another object of one or more embodiment of the present utility model is to provide one and has good The compressor of good lubricant effect.

Being also an object that of one or more embodiment of the present utility model provides a kind of structure letter Single, the with low cost and highly reliable fueller for compressor.

The another object of one or more embodiment of the present utility model is to provide one and includes State the compressor of fueller.

According to an aspect of the present utility model, it is provided that a kind of fueller for compressor, Including:

Pump, described pump is driven by the rotary shaft of described compressor, and described pump includes fuel feed hole and oil extraction Hole, described fuel feed hole is fluidly connected to the oil sump of described compressor, wherein, storage in described oil sump There is lubricating oil；

Oil supply gallery, described oil supply gallery includes that first end, described first end are fluidly connected to Described outage；And

Valve member, described valve member is arranged in described oil supply gallery, and described valve member is configured to Aperture change operation is carried out in response to the pressure differential of described valve member both sides.

Preferably, described valve member is configured to aperture change when the pressure differential in described valve member both sides becomes big Little and when the pressure differential of described valve member both sides diminishes aperture become big.

Preferably, described valve member is configured to when the pressure differential of described valve member both sides is more than or equal to the During one predetermined value, Guan Bi and the pressure differential when described valve member both sides are less than described first predetermined value Time open.

Preferably, described valve member includes spool, valve seat and flexible member, and described flexible member is even It is connected to described spool, with towards making described spool and the separate direction of described valve seat urge described valve Core, described valve member is configured so that: when the pressure differential of described valve member both sides is more than or equal to described During the first predetermined value, described spool engages with described valve seat；And when the pressure of described valve member both sides Difference is separated with described valve seat less than described spool during described first predetermined value.

Preferably, described valve seat and/or described spool include the oil allowing lubricating oil flow to pass through all the time Road.

Preferably, described spool include tapered portion, described tapered portion be constructed to be permeable to engage with valve seat and Separately.

Preferably, described pump includes pump accumulator, and described outage is via described pump accumulator fluid It is communicated to described oil supply gallery.

Preferably, described rotary shaft is provided with pump oil passage, described pump accumulator and described pump oil Passage.

Preferably, between described pump accumulator and described pump oil passage, it is additionally provided with pump accumulator to go out Mouthful, the outlet of described pump accumulator is sized to be chosen to regulate the lubrication flowing through described pump oil passage Flow-rate ratio between oil and the lubricating oil flowing through described oil supply gallery.

Preferably, described pump includes pump accumulator, and described outage is via described pump accumulator fluid Being communicated to described oil supply gallery, described valve member also includes and letting out that described pump accumulator is in fluid communication Putting passage, described leakage path is configured to when the pressure differential of described valve member both sides is more than or equal to releasing Described pump accumulator is made to be in fluid communication with described oil sump and when described valve member both sides during predetermined value Pressure differential be less than described in release predetermined value time make described pump accumulator and described oil sump disconnect to connect, Wherein, predetermined value of releasing described in is more than described first predetermined value.

Preferably, the second end contrary with described first end of described oil supply gallery is arranged on institute Stating near the air entry of compression mechanism of compressor, wherein, described compression mechanism is by described rotary shaft Drive.

Preferably, the second end contrary with described first end of described oil supply gallery is arranged on institute Stating near the main bearing seat of compressor, wherein, described main bearing seat is configured to support described rotary shaft.

Preferably, described oil supply gallery and described valve member are arranged in the housing of described compressor Side.

Preferably, described oil supply gallery and described valve member are arranged on outside the housing of described compressor Side.

According to another aspect of the present utility model, it is provided that a kind of compressor, described compressor includes Fueller mentioned above.

Preferably, described compressor is variable speed.

Preferably, described compressor is rotary compressor.

The advantage of the teaching according to one or more embodiments of the present utility model be following extremely Few one: be capable of only additionally supplying lubrication when the compressor slow-speed of revolution runs to parts to be lubricated Oil, solves the problem of lubrication deficient oil supply when the compressor slow-speed of revolution runs；Avoid compressor The problem of lubricating oil supply excess when high rotating speed runs；And it is not directed to such as controller, electromagnetic valve Etc. complicated, expensive device, simplify structure, reduce cost and improve reliability.

By explanation provided herein, other application will be apparent from.It should be understood that this Particular example and embodiment described in part are for illustration purposes only rather than attempt to limit this The scope of utility model.

Accompanying drawing explanation

Accompanying drawing as described herein is only in order at illustration purpose and is not intended to limit by any way Scope of the present utility model, accompanying drawing is not necessarily drawn to scale, and can zoom in or out some features with aobvious Show the details of particular elements.In the accompanying drawings:

Fig. 1 shows the profile of the compressor according to this utility model the first embodiment；

Fig. 2 shows the profile of the compressor according to this utility model the second embodiment；

Fig. 3 A shows the profile of the compressor according to this utility model the 3rd embodiment；

Fig. 3 B shows the enlarged drawing of dotted portion in Fig. 3 A；

Fig. 4 A shows the profile of the compressor according to this utility model the 4th embodiment；

Fig. 4 B shows the enlarged drawing of dotted portion in Fig. 4 A；

Fig. 5 shows the fueller for compressor according to each embodiment of this utility model Schematic diagram；

Fig. 6 A shows that the fuel feeding for compressor according to each embodiment of this utility model fills The profile put；

Fig. 6 B shows the amplification profile of dotted portion in Fig. 6 A；

Fig. 6 C shows the sectional view of the pump of the fueller of the dotted line A-A intercepting along Fig. 6 B；

Fig. 7 A shows that the fuel feeding for compressor according to this utility model preferred implementation fills The profile of the valve member put, wherein, spool is in an open position；

Fig. 7 B shows that the fuel feeding for compressor according to this utility model preferred implementation fills The profile of the valve member put, wherein, spool is in the close position；

Fig. 7 C shows the confession for compressor according to another preferred implementation of this utility model The profile of the valve member of oil device, wherein, spool is away from valve seat；

Fig. 7 D shows the confession for compressor according to another preferred implementation of this utility model The profile of valve member of oil device, wherein, spool enters at least partially near valve seat and spool Enter in the valve opening of valve seat；

Fig. 7 E shows the confession for compressor according to another preferred implementation of this utility model The profile of the valve member of oil device, wherein, spool engages with valve seat；

Fig. 8 shows the fueller for compressor according to each embodiment of this utility model Remodeling, wherein, it is shown that the leakage path being connected with valve member；And

Fig. 9 shows that the relation between the lubricating oil pressure in the rotating speed of rotary shaft and pump accumulator is bent Line, wherein, it is shown that the outlet of pump accumulator is two various sizes of situations.

Should be appreciated that in all these accompanying drawings, the instruction of corresponding reference number is similar or corresponding Part and feature.For purposes of clarity, all parts in accompanying drawing are not marked.

Detailed description of the invention

Hereafter description related to the preferred embodiment is the most only exemplary and be not intended to limit this reality With novel.

The basic structure of the compressor according to this utility model embodiment is described below with reference to Fig. 1 Make.Although fig 1 illustrate that be in the compressor of vertical position, it is to be understood that, this utility model Teaching can be applicable to be in the compressor of obliquity or horizontal level.

As it is shown in figure 1, compressor 1 includes substantially housing 10 in closed circular tubular, housing 10 Including being positioned at the main body 11 at middle part and being fixed to the top cover 12 at axial two ends and the bottom of main body 11 13.It is equipped with suction joint 14 on the main body 11, is used for sucking cold-producing medium, and at top cover 12 On be equipped with exhaust joint 15, for discharging the cold-producing medium after compression.At main body 11 and top cover 12 Between be additionally provided with the dividing plate 16 the most transversely extended, thus by compressor housing 10 Space, portion is separated into space, high-pressure side and low-pressure side space.Specifically, top cover 12 and dividing plate 16 it Between space, composition high-pressure side, space, and space between dividing plate 16 and bottom 13 constitutes low-pressure side Space.The bottom of housing 10 is also configured with the oil sump 17 for accommodating lubricating oil.

According to embodiment of the present utility model, it is equipped with compression mechanism 20 in low-pressure side space content With the drive mechanism 40 driving compression mechanism 20 via rotary shaft 30.As in the example shown in Fig. 1 In, compressor is the form of screw compressor, and compression mechanism 20 includes that be engaged with each other determines vortex Parts 22 and dynamic scroll element 24.It is positioned at the eccentric crank pin 32 of rotary shaft 30 upper end via lining Set (sign) is inserted in the hub portion 26 of dynamic scroll element 24, drives dynamic scroll portion to rotate Part 24.The top of rotary shaft 30 is supported by main bearing seat 50, and the bottom of rotary shaft 30 is by pair Bearing block 54 supports.Main bearing seat 50 and countershaft bearing 54 are fixing by the way of suitable to be connected To housing 10.Drive mechanism 40 for example, motor, it stator 42 including being fixed on housing 10 With the rotor 44 being fixed on rotary shaft 30.

Being provided with pump oil passage 34 in rotary shaft 30, pump oil passage 34 includes being positioned at the same of bottom Central hole 36 and the eccentric orfice 38 relative to concentric holes 36 radial deflection, concentric holes 36 is in fluid communication To oil sump 17, and eccentric orfice 38 extensions lead to the eccentric crank pin of rotary shaft 30 from concentric holes 36 32.Pump oil passage 34 under the power source effect such as oil pump by the lubricating oil in oil sump 17 upwards Guide, or be directly fed to parts to be lubricated, or carry to parts to be lubricated by means of cold-producing medium. Described parts to be lubricated can include compressing mechanism 20, main bearing seat 50 etc..

For compressor, its rotary shaft 30 at least can at the first rotating speed (in this article, Such as it is referred to alternatively as the slow-speed of revolution) and the second rotating speed (in this article, being such as referred to alternatively as high rotating speed) Lower operation, wherein, the first rotating speed is less than the second rotating speed.When compressor runs at the low rotational speed, The supply capability of pump oil passage 34 is more weak, being carried by cold-producing medium of can sucking of compression mechanism 20 The amount of lubricating oil is less.But, at the low rotational speed, owing to the pressure of such as back pressure cavity is relatively low etc. former Cause, more serious for the leakage situation higher rotation speed of compression chamber in scroll element, thus easily cause Deficient oil supply is lubricated under the slow-speed of revolution.I.e., at the low rotational speed, the portion to be lubricated to compressor is needed Part carries out extra lubricating oil supply.

On the contrary, when compressor runs at high speed, the supply capability of pump oil passage 34 is relatively By force, compression mechanism 20 can suck more lubricating oil carried by cold-producing medium so that under high rotating speed Lubricating oil is sufficient.Thus, at high speed, it is not necessary to treat lubricating component and carry out extra lubrication Oil supplies or only needs to treat lubricating component and carries out a small amount of lubricating oil supply, because too much lubrication Oil supply also may can cause degradation problem under heat exchanger efficiency.

For lubricating the problem of deficient oil supply under the slow-speed of revolution, in order to provide extra the most at the low rotational speed Lubricating oil supply, this utility model provide a kind of fueller for compressor 100 (see Fig. 5).

As shown in Figure 1 and Figure 5, fueller 100 includes pump 110, oil supply gallery 120 and valve Component 130 (see Fig. 5), wherein, pump 110 can be arranged on the lower end of rotary shaft 30 and by revolving Rotating shaft 30 drives, and oil supply gallery 120 one end and pump 110 are in fluid communication to receive by pump 110 pump The lubricating oil sent, its other end is arranged on nearby components to be lubricated, and valve member 130 is arranged on fuel feeding In passage 120 and be configured to open at the low rotational speed allow the lubricating oil pumped to flow through fuel feeding Passage 120 is to parts to be lubricated and closes at high speed to stop the lubricating oil pumped to flow through Oil supply gallery 120.Thus, this fueller 100 is capable of only inciting somebody to action in the case of slow-revving Lubricating oil supply in oil sump 17 is to parts to be lubricated.

As it is shown in figure 1, the lubricating oil pumped can be supplied to compressing mechanism by oil supply gallery 120 Near the air entry of 20.

Preferably, as it is shown in figure 1, oil supply gallery 120 can be arranged on inside housing 10.This Plant layout and can protect oil supply gallery 120 and the valve member 130 being arranged in oil supply gallery 120 Exempt to be affected by the external environment.

Alternatively, as in figure 2 it is shown, oil supply gallery 120 can be arranged on shell at least partially Outside body 10.This layout can be easily achieved fueller on the basis of existing product Set up improvement, be arranged on, because of oil supply gallery 120, the confession caused inside housing 10 without reply Interference problem between oil passage 120 and miscellaneous part.Additionally, this valve member 130 can also set Put being positioned in the part outside housing 10 at oil supply gallery 120, consequently facilitating to valve member 130 The monitoring performance of (or fueller 100) and maintenance if desired and replacing.

Preferably, fueller 100 can include multiple oil supply gallery 120, each oil supply gallery Each lubricating oil is supplied to corresponding parts to be lubricated.Specifically, Fig. 3 A and 3B shows The modification of the fueller shown in Fig. 1, wherein, oil supply gallery 120 includes that two are separated from each other Oil supply gallery: first end 122 that the first oil supply gallery includes being connected to pump 110 and will lubrication The second end 124 of the oil supply extremely air entry of compression mechanism 20；Second oil supply gallery includes connecting To the first end (not shown) of pump 110 and lubricating oil is supplied to the second of main bearing seat 50 End 126.

Similarly, Fig. 4 A and Fig. 4 B shows the modification of the fueller shown in Fig. 2, wherein, Oil supply gallery 120 includes being connected to the first end 122 of pump 110, by lubricating oil supply extremely compression The second end 124 of the air entry of mechanism 20 and by the of lubricating oil supply to main bearing seat 50 Three ends 126.In other words, oil supply gallery 120 includes two oil supply galleries: first end 122 With the second end 124 corresponding to the first oil supply gallery, and first end 122 and the 3rd end 126 Corresponding to the second oil supply gallery.It is appreciated that each oil supply gallery can have the first shared end Portion, it is possible to have respective first end.

Describe in detail according to each embodiment of this utility model below with reference to Fig. 5 to Fig. 9 Fueller 100 for compressor.

As it is shown in figure 5, fueller 100 includes pump 110, oil supply gallery 120 and valve member 130, wherein, oil supply gallery 120 one end is connected to pump 110 to allow pump 110 by grease pump Delivering to oil supply gallery 120, the other end can be arranged on the nearby components to be lubricated of compressor, valve structure Part 130 is arranged in oil supply gallery 120 to allow and stops lubricating oil to flow through oil supply gallery 120 and supplies Giving to nearby components to be lubricated, this valve member 130 is configured to when the pressure differential of valve member 130 both sides More than or equal to Guan Bi during the first predetermined value to stop lubricating oil be supplied to parts to be lubricated and work as Open to allow lubricating oil to be supplied to when the pressure differential of valve member 130 both sides is less than the first predetermined value Parts to be lubricated.

Specifically, when compressor runs at high speed, the supply capability of pump 110 is relatively strong, makes The pressure differential obtaining valve member 130 both sides is relatively large, and when compressor runs at the low rotational speed, The supply capability of pump 110 is more weak so that the pressure differential of valve member 130 both sides is relatively small.Therefore, Above-mentioned first predetermined value is construed as: valve member 130 both sides more than or equal to the first predetermined value The situation run at high speed corresponding to compressor of pressure differential, and valve member 130 both sides is little In the situation that the pressure differential of the first predetermined value is run at the low rotational speed corresponding to compressor.

In detailed description of the invention of the present utility model, as shown in Figure 6A, pump 110 can be arranged In the lower end of rotary shaft 30 and by rotary shaft 30, driving can be rotated.With reference to Fig. 6 B to 6C, pump 110 include fuel feed hole 114, outage 116 and pump rotor 118, wherein, the pump rotor of pump 110 118 operatings, to suck the lubricating oil in oil sump 17 and to be incited somebody to action by outage 116 from fuel feed hole 114 The lubricating oil sucked is expelled to oil supply gallery 120.

Preferably, so that sucking in oil sump 17 during pump 110 can be completely submerged in oil sump 17 Lubricating oil, it is also possible by means oil pipe (not shown) is fluidly connected to oil sump 17.

As described above, owing to valve member 130 is arranged in oil supply gallery 120, thus valve member Oil supply gallery 120 is divided into two section upstream parts and downstream part by 130.Specifically, Upstream portion is between pump 110 or first end 122 and valve member 130, and downstream part is positioned at Between valve member 130 and the second end 124.

When the compressor is operating, rotary shaft 30 rotates and drives pump 110 thus by the profit in oil sump 17 The upstream portion of oil supply gallery 120 delivered to by oil pump.When the rotating speed of rotary shaft 30 is relatively low, pump The pumpability of 110 (pressure of the lubricating oil such as pumped out or the flow of lubricating oil pumped out) Relatively low, thus in the upstream portion of oil supply gallery 120, set up relatively low lubricating oil pressure, (making the pressure differential of valve member 130 both sides less than the first predetermined value), lubricating oil can be via confession Oil passage 120 is supplied to parts to be lubricated.

On the other hand, when the rotating speed of rotary shaft 30 is bigger, the pumpability of pump 110 is relatively strong, makes Obtain the lubricating oil pressure in the upstream portion of oil supply gallery 120 of a relatively high, (make valve member 130 The pressure differential of both sides is more than or equal to the first predetermined value), lubricating oil can not be via oil supply gallery 120 It is supplied to parts to be lubricated.

It is pointed out that the downstream part of oil supply gallery 120 is empty with the low-pressure side of compressor all the time Between connect, thus in the case of the pressure loss in not considering oil supply gallery 120, oil supply gallery Lubricating oil pressure in the downstream part of 120 is substantially invariable, and is substantially equal to low-pressure side space Interior pressure, and the lubricating oil pressure in the upstream portion of oil supply gallery 120 is substantially equal to pump and discharges The pressure of lubricating oil.Therefore, the pressure differential of valve member 130 both sides can be substantially equal to pump and discharges pressure Difference between the pressure in the low-pressure side space of power and compressor.And pump discharge head is rotary shaft The function of rotating speed, accordingly, it is believed that valve member 130 enters only in response to the rotating speed of rotary shaft Row is opened and closed procedure.

So, achieve according to above-mentioned configuration of the present utility model: when rotary shaft 30 rotating speed relatively Time low (pressure differential making valve member 130 both sides is less than the first predetermined value) the most at the low rotational speed, Allow to parts fuel feeding to be lubricated, and (make the most at high speed when the rotating speed of rotary shaft 30 is higher Obtain the pressure differential of valve member 130 both sides more than or equal to the first predetermined value) time, stop to portion to be lubricated Part fuel feeding.Which solve compressor part under the slow-speed of revolution, for the problem of shortage of oil, to prevent at height simultaneously Fuel feeding excess under rotating speed.

Based on the actual application requirements, it may be determined that the first predetermined value that valve member 130 is opened and closed. For example, it is possible to based on the actual application requirements, when determining generation lubrication deficient oil supply, rotary shaft faces Boundary's rotating speed, then measure the pump discharge head under this critical speed, thus calculate first and make a reservation for Value.Then, corresponding valve member is being selected according to the first predetermined value.However, it is possible under there will be State rough sledding: according to the first predetermined value having calculated that, it is impossible to or be difficult to find and match Valve member, this is accomplished by after determining critical speed, suitably regulates the size of pump discharge head, To adapt to existing valve member.

Hereinafter the regulation of the first predetermined value (or pump discharge head) will be described in detail.

In preferred implementation of the present utility model, as shown in Figure 6B, pump 110 also includes pump Accumulator 112, pump accumulator 112 is arranged on outage 116 and the oil supply gallery 120 of pump 110 Between, such as it is arranged on the lower section of outage 116 so that the lubricating oil pumped is entering fuel feeding Can accumulate in pump accumulator 112 before passage 120.Lubrication pressure in pump accumulator 112 Power is considered pump discharge head, it is thus possible to make pump discharge head more steady.In rotation (such as equal to critical speed) in the case of the rotating speed of rotating shaft 30 is constant, pump accumulator can be regulated Pressure in 112, to be adapted to the specification of existing valve member.

For example, it is possible to arrange pressure transducer in pump accumulator 112 to monitor pump accumulator 112 Interior lubricating oil pressure.First, the critical of generation lubricating oil deficiency is determined according to real work demand Rotating speed, then calculates pump storage according to the specification (corresponding to the first predetermined value) of existing valve member The pressure that grease chamber 112 planted agent reaches, then when the rotating speed of rotary shaft 30 is equal to critical speed, (example As by the operation such as the lubricating oil in pump accumulator 112 is released) by the profit in pump accumulator 112 Lubricating oil pressure (i.e. pump discharge head) regulation is to the above-mentioned pressure that should reach.

It is pointed out that and can also select the rule of suitable valve member according to practical operation demand Lattice, the specification of oil supply gallery and pump size etc..

Preferably, the pump oil passage 34 that pump 110 can also be configured to compressor pumps lubricating oil. Specifically, as shown in Figure 6B, the pump accumulator 112 of pump 110 is fluidly connected to pump oil passage 34 Concentric holes 36.

This layout makes pump oil passage 34 and oil supply gallery 120 share a pump 110 so that compression The structure of machine is simpler compact.

It is highly preferred that the lower end of rotary shaft 30 can be provided with eccentric driving part 35, this bias is driven One end (upper end as shown in Figure 6B) of moving part 35 be fixedly attached to rotary shaft 30 and with one of Body ground rotates, and the other end (lower end as shown in Figure 6B) is mounted slidably in an eccentric manner In the pump rotor 118 of pump 110 (as shown in Figure 6 C), to drive pump rotor 118.This bias The connecting hole 39 in through-hole form can be provided with in actuator 35, with by pump accumulator 112 with Concentric holes 36 is in fluid communication.

It is highly preferred that as shown in figs. 6b and 6c, pump accumulator 112 also includes that pump accumulator exports 113, the outlet of this pump accumulator 113 between pump accumulator 112 and connecting hole 39, it is thus possible to Enough play throttling action.Specifically, aperture or the size of this pump accumulator outlet 113 is optional , or this pump accumulator outlet 113 be easy for change, be suitable for regulation and flow through pump oil passage Flow-rate ratio between lubricating oil and the lubricating oil flowing through oil supply gallery 120 of 34.Pump accumulator exports The aperture of 113 or the selection of size or replacing can regulate pump discharge head, it is also possible to regulation pump storage The pump discharge head in grease chamber 112 responding ability to the rotation speed change of rotary shaft 30.

Specifically, the first less aperture (for example, 2mm) of pump accumulator outlet 113 can drop Lubricating oil in low pump accumulator 112 flows into the amount of concentric holes 36 so that in pump accumulator 112 Lubricating oil pressure along with rotary shaft 30 rotating speed increase and relatively quickly increase.

By comparison, the second bigger aperture (for example, 5mm) meeting of pump accumulator outlet 113 Increase the lubricating oil in pump accumulator 112 and flow into the amount of concentric holes 36 so that pump accumulator 112 Interior lubricating oil pressure increases along with the rotating speed of rotary shaft 30 and will be relatively slowly increases.

Especially, Fig. 9 shows aperture size the turning rotary shaft 30 of pump accumulator outlet 113 The impact of the relation between lubricating oil pressure in speed and pump accumulator 112.As it is shown in figure 9, work as When the aperture of pump accumulator outlet 113 is 2mm (the first less aperture), pump accumulator 112 Interior lubricating oil pressure is higher, and this lubricating oil pressure is with the increase of rotary shaft 30 rotating speed promptly Increase.Ground can be contrasted, when the aperture of pump accumulator outlet 113 is 5mm (bigger the Two apertures) time, the lubricating oil pressure in pump accumulator 112 is relatively low, and this lubricating oil pressure is with rotation Rotating shaft 30 rotating speed increases and increases lentamente.Thus, it is possible to by regulation pump accumulator outlet 113 Aperture adapt to range of application and the sensitivity of valve member 130.

On the other hand, in the aperture of pump accumulator outlet 113 diminishes and can hinder pump accumulator 112 Lubricating oil enters concentric holes 36, thus reduces by the supply of pump oil passage 34 to parts to be lubricated Lubricants capacity or ratio, on the contrary, increase by oil supply gallery 120 supply to portion to be lubricated The lubricants capacity of part or ratio.Thus, by selecting or change the aperture of pump accumulator outlet 113 Or size, it is possible to reasonably distribute quantity delivered or the ratio of each lubricating oil feed path, it is achieved profit The optimal supply of lubricating oil.

Fig. 7 A to Fig. 7 B shows the fuel feeding for compressor according to this utility model embodiment The example of the valve member 130 of device 100.Valve member 130 can include substantially cylindrical valve Housing 131, the first end plate 134 being fixed on the axial two ends of valve chest 131 and the second end plate 136, The spool 132 that is contained in valve chest 131 and be arranged on spool 132 and the first end plate 134 it Between elastic component 138.Valve chest the 131, first end plate 134 and the second end plate 136 define The inner space of valve member 130.It is provided with and the upstream of oil supply gallery 120 on first end plate 134 First valve opening 135 of partial fluid communication, to allow the lubricating oil pumped to flow into valve member 130 Inner space；The downstream part fluid with oil supply gallery 120 it is provided with even on second end plate 136 The second logical valve opening 137, the inner space of the outflow of lubrication oil valve member 130 to allow flow into.

Valve member 130 can be normally open type valve (as shown in figs. 7 a-b), and Fig. 7 A shows Valve member 130 is in the situation of non-mode of operation, and now, elastic component 138 does not bears any load Lotus such as compressive load and tensile load.When fueller 100 operates, lubricating oil is via First valve opening 135 of end plate 134 flows into the inner space of valve member 130.The lubricating oil flowed into Impact spool 132 thus spool 132 is pushed towards the second end plate 136.When rotary shaft 30 Rotating speed relatively low the most at the low rotational speed time, lubricating oil is less to the impact of spool 132, and spool 132 is not Engaging with the second end plate 136, this allows lubricating oil to flow through the second valve opening 137 and leaves valve member 130. Along with the rotating speed of rotary shaft 30 constantly increases, spool 132 is eventually in the percussion of lubricating oil Lower engage with the second end plate 136, now, the second end plate 136 as valve seat, with spool 132 The incompatible prevention lubricating oil that matches flows through the second valve opening 137, as shown in Figure 7 B.This configuration achieves When the rotating speed of rotary shaft 30 is higher, valve member 130 closes, and then stops lubricating oil via confession Oil device 100 supply is to parts to be lubricated.It is pointed out that the valve member according to the application also Being not limited to (as described above) is constructed to respond to the pressure differential (rotary shaft of valve member both sides Rotating speed) and carry out closing and opening operation, but can be also configured in response to valve member both sides Pressure differential and carry out aperture change operation.

Such as, can be also configured to the pressure in described valve member both sides according to the valve member of the application When difference becomes big, aperture diminishes and aperture becomes big when the pressure differential of valve member both sides diminishes.

Specifically, Fig. 7 C to 7E shows the fuel feeding of another preferred implementation according to the application The valve member of device, the configuration of this valve member and the valve member substantially phase shown in Fig. 7 A to 7B With, therefore identical structure is not repeated.As seen in figure 7 c, the spool 132 of valve member 130 Including tapered portion 133, this tapered portion 133 be arranged on spool 132 towards the second end plate 136 (i.e. Valve seat) side, engage for the second end plate 136.Fig. 7 C shows valve member 130 Being in the situation of non-mode of operation, now, elastic component 138 does not bears any load such as pressure Contracting load and tensile load.When fueller 100 operates, lubricating oil is via the first end plate 134 The first valve opening 135 flow into the inner space of valve member 130.The lubricating oil impact spool 132 flowed into Thus spool 132 is pushed towards the second end plate 136.I.e. exist when the rotating speed of rotary shaft 30 is relatively low Time under the slow-speed of revolution, lubricating oil is more weak to the percussion of spool 132, and spool 132 is only oriented towards second End plate 136 moves but does not engages with the second end plate 136, and this allows lubricating oil to flow through the second valve opening 137 Leave valve member 130.Along with the rotating speed of rotary shaft 30 increases, the percussion of lubricating oil increases, Spool 132 is moved, when spool 132 is near the second end plate further towards the second end plate 136 136 but when not yet engaging with the second end plate 136 (as illustrated in fig. 7d), the tapered portion of spool 132 133 can enter in the second valve opening 137 at least partially so that the permission of the second valve opening 137 The effective cross-sectional area that lubricating oil flow passes through reduces, i.e. the aperture of valve member 130 reduces, from And the flow of the flowing lubricating oil by valve member 130 is reduced.Along with turning of rotary shaft 30 Speed constantly increases, spool 132 (tapered portion 133) eventually under the percussion of lubricating oil with Second end plate 136 (valve seat) engages, thus stops lubricating oil to flow through the second valve opening 137, such as figure Shown in 7E.This configuration achieves: when the rotating speed of rotary shaft 30 increases, opening of valve member 130 Degree diminishes, and then preferably reduces the lubricating oil via fueller 100 supply to parts to be lubricated Flow；Along with the rotating speed of rotary shaft 30 increases further, valve member 130 closes, and then resistance Only lubricating oil is via fueller 100 supply extremely parts to be lubricated.

Although having been described with the valve member according to the application in the preferred implementation of the application, But it is not limited thereto, but the valve member of all following types, described type can also be included Valve member can be configured to the pressure differential in response to valve member both sides and carry out aperture change operation. Especially, the valve member of described type can be configured to open when the pressure differential in valve member both sides becomes big Degree diminishes and aperture becomes big when the pressure differential of valve member both sides diminishes.

In other preferred implementations of the application, described valve member can be also configured to along with valve The pressure differential of component both sides becomes larger and its aperture is tapered into, especially so that flow through The flow of the lubricating oil of described valve member is gradually reduced.

In a preferred embodiment, oil duct can be offered on the second end plate 136 and/or spool 132 (not shown) so that still allow for lubricating oil (such as a small amount of lubricating oil) with spool when end plate engages Flow through valve member 130 to supply.This can also ensure height when such as other fuel supply paths lost efficacy Lubricating oil supply under rotating speed.

In a preferred embodiment, as shown in Figure 8, fueller 100 can also include releasing logical Road 140.Leakage path 140 can be in fluid communication with pump accumulator 112, with at pump accumulator 112 Lubricating oil is released to oil sump 17 time too high by interior lubricating oil pressure.

Specifically, leakage path 140 can be provided with normally close valve (not shown).This normally close valve Just can open valve member 130 closes when.Especially, this normally close valve is configured at valve member The pressure differential of 130 both sides more than or equal to release predetermined value time just open, wherein, this predetermined value of releasing More than above-mentioned first predetermined value, thus prevent because of valve member 130 close after valve member 130 and/or Lubricating oil pressure moment in pump accumulator 112 rise and to valve member 130, oil supply gallery 120 And/or pump 110 causes damage.

As shown in Figure 8, the first end 142 of leakage path 140 can be connected to valve member 130 Such as being connected to the valve chest 131 of valve member 130, its second end 144 can be with oil sump 17 Fluid communication.

In other substituting preferred implementations, the first end 142 of leakage path 140 is permissible It is connected to pump accumulator 112 or the upstream portion of oil supply gallery 120.

It is pointed out that compressor according to this utility model embodiment including, but not limited to Screw compressor；The pump for the fueller of compressor according to this utility model embodiment can To be positive displacement pump, such as impeller pump.

Valve member according to the fueller for compressor of the present utility model can be the purest Mechanical valve component, i.e. can not rely on and such as controls the complex and expensive such as device, calutron Device but only the rotating speed (or pressure differential of valve member both sides) of rotary shaft is responded and carries out Open the valve member with closed procedure, this simplify structure, reduce cost, and improve reliable Property.

But, do not limit to according to the valve member for the fueller of compressor of the present utility model In Purely mechanical valve member.Alternatively, valve member of the present utility model also may incorporate such as Control the auxiliary device such as device, electronic device, calutron, sensing element to perform to open and close Closing operation.

More importantly, the slow-speed of revolution is overcome according to the fueller for compressor of the present utility model The lower defect for shortage of oil.

Although in preferred implementation described herein, for the valve structure of the fueller of compressor Part be described as being configured to when the pressure differential of valve member both sides is more than or equal to the first predetermined value Guan Bi with And open when the pressure differential of valve member both sides is less than the first predetermined value, but teaching of the present utility model is also It is not limited to this.Especially, according to the valve structure of the fueller for compressor of the present utility model Part can be also configured to the pressure differential in response to valve member both sides or differential pressure range and carries out aperture change Change operation.These remodeling and modification can be obtained based on the actual application requirements by those skilled in the art Arrive, and each fall within the range of this utility model taught.

It is appreciated that the compressor according to the application can include variable speed compressor, this variable speed pressure The rotating speed of the rotary shaft of contracting machine is variable and includes at least two working speed.Such as, this variable speed Compressor includes frequency-changeable compressor.

It is further appreciated that the compressor according to the application is possible not only to include such as screw compressor etc Rotary compressor, it is also possible to include reciprocating compressor.

It is pointed out that the ginseng of the directional terminology such as such as front, back, left, right, up, down in literary composition Examine merely for the purpose described, not to embodiment of the present utility model side in actual applications It is construed as limiting to orientation.

Although described various embodiment of the present utility model in detail at this, it should be appreciated that, This utility model is not limited to the detailed description of the invention describing in detail here and illustrating, without departing from this Other is may be effected by one skilled in the art in the case of the connotation of utility model and scope Modification and remodeling.All these modification and remodeling each fall within the range of this utility model.

Reference numerals list

1 compressor

10 housings

11 main bodys

12 top covers

13 bottoms

14 suction joint

15 exhaust joints

16 dividing plates

17 oil sumps

20 compression mechanisms

22 determine scroll element

24 move scroll element

26 hub portions

30 rotary shafts

32 eccentric crank pins

34 pump oil passages

35 eccentric driving part

36 concentric holes

38 eccentric orfices

39 connecting holes

40 drive mechanisms

42 stators

44 rotors

50 main bearing seats

54 countershaft bearings

100 fuellers

110 pumps

112 pump accumulators

113 pump accumulator outlets

114 fuel feed holes

116 outages

118 pump rotors

120 oil supply galleries

122 first ends

124 the second ends

126 the second ends, the 3rd end

130 valve members

131 valve chests

132 spools

133 tapered portion

134 first end plates

135 first valve openings

136 second end plates

137 second valve openings

138 elastic components

140 leakage paths

142 first ends

144 the second ends.

Claims (17)

1. the fueller for compressor, it is characterised in that including:

Pump, described pump is driven by the rotary shaft of described compressor, and described pump includes fuel feed hole and oil extraction Hole, described fuel feed hole is fluidly connected to the oil sump of described compressor, wherein, storage in described oil sump There is lubricating oil；

Oil supply gallery, described oil supply gallery includes that first end, described first end are fluidly connected to Described outage；And

Valve member, described valve member is arranged in described oil supply gallery, and described valve member is configured to Aperture change operation is carried out in response to the pressure differential of described valve member both sides.

Fueller for compressor the most according to claim 1, wherein, described valve member It is configured to aperture when the pressure differential in described valve member both sides becomes big diminish and at described valve member two When the pressure differential of side diminishes, aperture becomes big.

Fueller for compressor the most according to claim 1, wherein, described valve member It is configured to when the pressure differential of described valve member both sides is more than or equal to the first predetermined value close and work as institute Open when stating the pressure differential of valve member both sides less than described first predetermined value.

Fueller for compressor the most according to claim 3, wherein, described valve member Including spool, valve seat and flexible member, described flexible member is connected to described spool, with towards making Stating spool and urge described spool with the separate direction of described valve seat, described valve member is configured so that: when The pressure differential of described valve member both sides is more than or equal to described spool during described first predetermined value and described valve Seated connection closes；And when described valve member both sides pressure differential less than described first predetermined value time described spool Separate with described valve seat.

Fueller for compressor the most according to claim 4, wherein, described valve seat and / or described spool include the oil duct that allows lubricating oil flow to pass through all the time.

Fueller for compressor the most according to claim 4, wherein, described spool bag Including tapered portion, described tapered portion is constructed to be permeable to engage with valve seat and separate.

Fueller for compressor the most according to claim 1, wherein, described pump includes Pump accumulator, described outage is fluidly connected to described oil supply gallery via described pump accumulator.

Fueller for compressor the most according to claim 7, wherein, described rotary shaft In be provided with pump oil passage, described pump accumulator and described pump oil passage.

Fueller for compressor the most according to claim 8, wherein, stores up at described pump The outlet of pump accumulator, the chi of described pump accumulator outlet it is additionally provided with between grease chamber and described pump oil passage Very little can be chosen to regulate flow through the lubricating oil of described pump oil passage and the profit flowing through described oil supply gallery Flow-rate ratio between lubricating oil.

Fueller for compressor the most according to claim 3, wherein, described pump bag Including pump accumulator, described outage is fluidly connected to described oil supply gallery, institute via described pump accumulator Stating valve member also to include and the leakage path of described pump accumulator fluid communication, described leakage path constructs Become when described valve member both sides pressure differential more than or equal to release predetermined value time make described pump accumulator with Described oil sump fluid communication and predetermined value of releasing described in being less than when the pressure differential of described valve member both sides Time make described pump accumulator and described oil sump disconnect connect, wherein, described in predetermined value of releasing be more than described First predetermined value.

11. according to the fueller for compressor described in any one in claim 1 to 10, Wherein, the second end contrary with described first end of described oil supply gallery is arranged on described compressor Compression mechanism air entry near, wherein, described compression mechanism driven by described rotary shaft.

12. according to the fueller for compressor described in any one in claim 1 to 10, Wherein, the second end contrary with described first end of described oil supply gallery is arranged on described compressor Main bearing seat near, wherein, described main bearing seat is configured to support described rotary shaft.

13. according to the fueller for compressor described in any one in claim 1 to 10, Wherein, described oil supply gallery and described valve member are arranged on the case inside of described compressor.

14. according to the fueller for compressor described in any one in claim 1 to 10, Wherein, described oil supply gallery and described valve member are arranged on the hull outside of described compressor.

15. 1 kinds of compressors, it is characterised in that described compressor includes according to claim 1 to 14 In the fueller for compressor described in any one.

16. compressors according to claim 15, wherein, described compressor is variable speed.

17. compressors according to claim 16, wherein, described compressor is rotary compression Machine.